JP2006125511A - Power transmission device, and grinder and agitator using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power transmission device having novel construction using a reciprocating slider crank mechanism as an application for outputting the power of non-constant speed rotating motion, and to provide a grinder and an agitator using the same for finely and uniformly crushing ground objects into pieces in a relatively shorter time and for homogeneously mixing/agitating agitated objects in a relatively shorter time, respectively. <P>SOLUTION: A driven shaft 23 of the power transmission device 1 has reciprocating linear motion together with a sliding portion 14 and an articulated arm 17. The driven shaft 23 also has non-constant speed rotating motion at a composite angular speed which is composed of the rotating angular speed of constant rotating motion transmitted from a driving shaft 21 via a gear transmission mechanism 20 (a driving side small gear 22 and a driven side large gear 24) and a rocking angular speed based on the reciprocating rocking motion of the articulated arm 17 around a supporting shaft 16 (an axis O3) of a slider 15. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a novel power transmission device to which a reciprocating slider crank mechanism (or an offset crank mechanism) is applied. Further, a crushing device for crushing and mixing a solid lump into fine and uniform powdery (dry) or slurry (wet) fragments using such a power transmission device, for example, with a mortar and pestle. And a stirrer for homogeneously mixing and stirring substances such as powder (dry) and slurry (wet).

  For example, a mortar has been widely used in the past in order to uniformize the particle size of a sample for composition determination in a laboratory or to mix a plurality of drugs uniformly in a pharmaceutical process. At that time, mortar and pestle containing crushed materials such as chemicals and chemicals were manually squeezed in the old days, but at present, the mortar and / or pestle is driven by the rotational driving force of an electric motor or the like. A rotating mechanism (commonly referred to as “automatic mortar”) is frequently used (see, for example, Patent Documents 1 to 3). However, in these crushing devices, the mortar and pestle are rotated at a constant speed, so that the crushing object in the mortar is easy to be carried along with the pestle (easy to escape), and is finely and uniformly fragmented in a short time. It may be difficult to be done.

JP-A-6-320041 JP 2002-306986 A JP 2002-316065 A

  On the other hand, a reciprocating slider crank mechanism (and an offset crank mechanism) is widely used as a mechanism having a power transmission function and a linear motion-rotational motion conversion function, and a typical example thereof is an engine piston-crank mechanism. As is well known, the reciprocating slider crank mechanism (offset crank mechanism) is a simple mechanism including a rotating crank arm, a reciprocating linearly moving slider (piston), and a connecting rod connecting the two. Therefore, for example, as shown in Patent Document 4, basically, the rotational movement of the crank arm or the reciprocating linear movement of the slider is merely taken out and used as it is. For example, as shown in Patent Document 5, it is also known that the connecting rod is divided into two to make a quick return mechanism. However, because of the simple configuration, a new power transmission device is incorporated by incorporating another mechanism or the like. Almost no ingenuity has been made.

JP-A-6-201010 JP 2000-291760 A

  The subject of this invention is providing the power transmission device which has the novel structure which applied the reciprocating slider crank mechanism (or offset crank mechanism), and can take out the power of non-constant speed rotational motion. Another object of the present invention is to use such a power transmission device to crush the object to be ground finely and uniformly in a relatively short time, and to homogenize the stirring object in a relatively short time. And a stirring device capable of mixing and stirring.

Means for Solving the Problems and Effects of the Invention

In order to solve the above-described problem, a power transmission device according to the present invention includes:
An eccentric rotating part in which the crank arm rotates away from the drive shaft by a predetermined distance, a slide moving part in which the slider reciprocates on a straight line, a support shaft of the crank arm, and a support shaft of the slider are respectively rotatable. A reciprocating slider crank mechanism or an offset crank mechanism, each having a reciprocating linearly reciprocating motion with the slide moving portion while reciprocatingly reciprocatingly swinging around a support shaft of the slider,
A driving shaft that is rotatably supported by the oscillating connecting portion, and that rotates around the drive shaft in synchronization with the rotating motion of the crank arm of the eccentric rotating portion, and is arranged in parallel with the driving shaft; A rotation shaft that is rotatably supported by the oscillating joint, and a rotational transmission mechanism that transmits rotational motion from the driving shaft to the driven shaft;
With
The driven shaft performs a reciprocating linear motion together with the slide moving portion and the oscillating connecting portion, and the rotational angular velocity of the rotational motion transmitted from the driving shaft via the rotational transmission mechanism and the support shaft of the slider are centered. The oscillating joint portion performs an inconstant speed rotational motion having a combined angular velocity combined with a swing angular velocity based on a reciprocating swing motion of the swing connecting portion.

  In this power transmission device, there is a rotational transmission mechanism that transmits rotational motion from a driving shaft that rotates synchronously with a crank arm of a reciprocating slider crank mechanism or an offset crank mechanism to a driven shaft that is rotatably supported by a swinging connecting portion. It has been incorporated. As a result, the driven shaft is a combined angular velocity obtained by combining the reciprocating linear motion by the reciprocating slider crank mechanism, the rotational angular velocity of the rotational motion transmitted from the driving shaft, and the swing angular velocity based on the reciprocating swing motion of the swing joint. And an inconstant speed rotational movement having In other words, the driven shaft that is pivotally supported by the oscillating connecting portion is newly added to the non-uniform speed in addition to the reciprocating linear motion obtained from the reciprocating slider crank mechanism (this also corresponds to a kind of non-uniform linear motion). Since the rotary motion is performed, if an operating device is connected using the driven shaft as an output take-out shaft, a novel operating mode, function, application, etc. can be given to the operating device. In addition, since such a power transmission device can be configured simply by incorporating a rotary transmission mechanism including a driving shaft and a driven shaft into a reciprocating slider crank mechanism or the like, a new power transmission device can be obtained in a compact, compact and inexpensive manner. .

  For example, when a mortar of a crushing device (automatic mortar) is placed and fixed on a driven shaft (output take-out shaft) arranged in the vertical direction, the mortar performs a reciprocating linear motion and an inconstant speed rotational motion. The crushed object in the mortar becomes easy to mix by changing the rotation speed of the mortar (change in the synthetic angular velocity), and the crushed object is fine and uniform in a relatively short time (dry type) or slurry (wet type) Can be broken into pieces. Alternatively, when the container of the stirrer is placed and fixed on the driven shaft (output take-out shaft) arranged in the vertical direction, the container performs reciprocating linear motion and inconstant speed rotation motion, whereby the powder in the container Stirring objects such as liquid (dry) and slurry (wet) can be easily mixed by changing the rotation speed of the container (changing the synthetic angular velocity), and the stirring objects can be mixed and stirred uniformly in a relatively short time. .

In order to solve the above-mentioned problem, a specific mode of the power transmission device according to the present invention is as follows.
An eccentric rotating part in which the crank arm rotates at a constant speed away from the drive shaft at a constant speed, a slide moving part in which the slider reciprocates on a straight line perpendicular to the axis of the drive shaft, a support shaft of the crank arm, and the A reciprocating reciprocating portion having a support shaft of the slider rotatably and parallel to each other, and a reciprocating reciprocating motion about the support shaft of the slider and a reciprocating linear motion together with the slide moving portion. A slider crank mechanism;
It is integrated with the support shaft of the crank arm that is rotatably supported by the rocking connecting portion, and performs constant speed rotation around the drive shaft at the same period as the constant speed rotation of the crank arm of the eccentric rotation portion. The drive shaft is arranged in parallel with the drive shaft and concentrically with the support shaft of the slider rotatably supported by the swing connecting portion, and is rotatably supported by the swing connecting portion. A rotation transmission mechanism that transmits a constant speed rotation motion from the driving shaft to the driven shaft,
With
While the driven shaft performs a reciprocating linear motion that reciprocates once every cycle in which the driving shaft rotates once, together with the slide moving portion and the swing connecting portion,
(1) In the cycle, the rotational motion of the driven shaft is transmitted from the driving shaft via the rotational transmission mechanism in the direction of the swinging motion of the swinging connecting portion around the support shaft of the slider. In the first swing range that is the same direction as the direction, the rotational angular velocity of the constant speed rotational motion transmitted from the driving shaft is combined with the swing angular velocity based on the reciprocal swing motion of the swing joint. To perform a non-uniform rotational motion with an increased combined angular velocity,
(2) Of the one cycle, in the second swing range in which the swing motion direction of the swing joint is opposite to the rotational motion direction of the driven shaft, the rotational angular velocity of the constant speed rotational motion is In addition, an inconstant speed rotational motion having a combined angular velocity that is decelerated by being combined with a swing angular velocity based on the reciprocating swing motion is performed.

  In this power transmission device, an oscillating connecting portion is arranged concentrically with a support shaft of a slider from a driving shaft that is integrated with a support shaft of a crank arm of a reciprocating slider crank mechanism and rotates at the same speed as the crank arm. A rotation transmission mechanism for transmitting a constant speed rotation motion is incorporated into a driven shaft that is rotatably supported by the motor. As a result, the driven shaft is a combination of the reciprocating linear motion by the reciprocating slider crank mechanism and the rotational angular velocity of the constant speed rotational motion transmitted from the driving shaft and the swing angular velocity based on the reciprocating swing motion of the swing joint. An inconstant speed rotational motion having an angular velocity is performed simultaneously. In other words, in addition to the reciprocating linear motion obtained from the reciprocating slider crank mechanism, the driven shaft that is pivotally supported by the oscillating connecting portion newly has an area where the combined angular velocity is increased (acceleration area) and an area where the combined angular velocity is increased (deceleration area). Therefore, if an operating device is connected using the driven shaft as an output extraction shaft, a novel and dynamic operating mode, function, application, etc. can be given to the operating device. In addition, since such a power transmission device can be configured simply by incorporating a rotary transmission mechanism including a driving shaft and a driven shaft into the reciprocating slider crank mechanism, a new power transmission device can be obtained in a small, compact and inexpensive manner.

  In the second swing range (that is, the deceleration region), a reversal region (where the combined angular velocity of the driven shaft is reversed between positive and negative when the swing angular velocity based on the reciprocating swing motion exceeds the rotational angular velocity of the constant speed rotary motion ( In some cases, a reverse rotation region) is partially included. By forming such a reversal region (region where the driven shaft rotates reversely) in the second swing range of the swing joint corresponding to the area (deceleration region) where the combined angular velocity of the driven shaft is decelerated. For example, in the crushing apparatus, the object to be crushed can be broken into fine and uniform powder (dry) or slurry (wet) in a shorter time. Moreover, in the stirring device, the stirring target can be uniformly mixed and stirred in a shorter time.

  In these power transmission devices, the rotation transmission mechanism is any one of a contact transmission mechanism using a gear, a friction wheel, etc., and a winding transmission mechanism using a belt, rope, wire, chain, etc. Also good.

  Of these, when the rotational transmission mechanism is constituted by a gear transmission mechanism in which a driving side small gear fixed to the driving shaft and a driven side large gear fixed to the driven shaft are meshed, the rotation from the driving shaft to the driven shaft The power transmission rate can be improved by reducing the transmission loss. In addition, since the rotational angular velocity from the driving shaft to the driven shaft is decelerated via the rotational transmission mechanism (gear transmission mechanism), the rotational speed change of the driven shaft (synthetic angular speed increase / decrease change) by combining with the swing angular velocity is It becomes relatively small and stress concentration on the driven shaft can be alleviated.

Next, in order to solve the above-mentioned problem, the crushing device according to the present invention is:
Such a power transmission device,
A rotational drive source such as an electric motor that rotationally drives a drive shaft arranged in the vertical direction;
Placed and fixed at the upper end of the driven shaft arranged in the vertical direction, and performs the reciprocating linear motion and non-uniform speed rotation motion with the driven shaft, like a mortar (for example, the upper part is opened) A bowl-shaped container containing objects;
When the bowl-like container performs reciprocating linear motion and inconstant speed rotation movement, it is at least temporarily in contact with the inner surface thereof to crush and crush the object to be crushed into fragments, ,
It is characterized by providing.

  According to such a crushing apparatus, a crushing container (mortar) performs a reciprocating linear motion and an inconstant rotational movement, whereby a crushing object in the crusted container changes in the rotational speed of the bowl-shaped container ( It becomes easy to mix due to the change in the synthetic angular velocity, and the object to be crushed can be crushed into a fine and uniform powder (dry) or slurry (wet) in a relatively short time. Therefore, a compact, compact and inexpensive grinding device can be obtained.

  At this time, the crushed body (pestle) is always in contact with the inner surface of the bowl-shaped container while the bowl-shaped container performs the reciprocating linear motion and the non-uniform rotation motion, and the axis of the driven shaft in plan view. It is desirable that the main body part (main body casing) is fixedly disposed and pressed downward so as to be positioned on the reciprocating linear motion trajectory or the extension thereof. As a result, the crushing body moves relative to the bowl-shaped container on the reciprocating linear motion locus of the axis of the driven shaft or on its extension. Therefore, for example, if the axis of the bowl-shaped container and the axis of the driven shaft are matched, the relative movement stroke of the crushed body with respect to the bowl-shaped container can be increased to the full inner diameter of the bowl-shaped container. The object to be crushed can be crushed by using the inner surface extensively. If the inner bottom surface of the bowl-shaped container and the outer peripheral surface of the lower end portion of the crushed body are each formed in a hemispherical shape, the lower end part of the crushed body is always in contact (pressed) with the inner surface of the bowl-shaped container. However, the reciprocating linear motion and the non-uniform rotation motion of the bowl-shaped container are smoothly performed, and wear and the like of both can be suppressed.

  Further, when the bowl-shaped container performs reciprocating linear motion and non-uniform speed rotation motion, at least temporarily contacts the inner surface of the bowl-shaped container and stirs the debris of the ground object to be ground by the ground body. In some cases, a stirring body such as a spatula is disposed near the crushing body (positioned and fixed to the main body (main body casing)). By positioning the stirrer (scalpel) in the vicinity of the crushed body, the stirrer can immediately act on the debris of the crushed object immediately after being crushed by the crushed body. The object to be crushed can be finely and uniformly fragmented in a shorter time.

  Specifically, the stirrer is in contact with the wall of the bowl-shaped container between the crushing body and the wall of the bowl-shaped container that are close to each other in the speed increasing region in the non-uniform rotation of the bowl-shaped container. It is good to receive the debris of the crushing target object which is located in the form to be crushed by them (the crushing body and the bowl-shaped container) and guide it toward the center of the bowl-shaped container. By grinding the crushed body and the bowl-shaped container in the speed-up area (high-speed rotation area) of the bowl-shaped container, the object to be crushed is fragmented at the highest speed and efficiently finely and uniformly. Since it is received by the stirring body and guided (returned) to the central portion of the bowl-shaped container, the object to be crushed is subjected to the crushing action and the stirring action most efficiently. In addition, since the crushed pieces are mixed with the reduced-speed rotation (deceleration region or reversal region) of the bowl-like container substantially simultaneously with or after being guided to the central part of the bowl-like container by the stirring body, the next cycle The crushing action and the stirring action can be smoothly exerted. In particular, in the case of the wet type in which slurry-like debris is crushed and mixed, the stirrer is used for the slurry-like debris after crushing that tends to adhere along the inner surface of the wall of the bowl-like container. The action of scraping to the side becomes remarkable.

On the other hand, in order to solve the above problem, the stirring device according to the present invention is:
Such a power transmission device,
A rotational drive source such as an electric motor that rotationally drives a drive shaft arranged in the vertical direction;
Placed and fixed at the upper end of the driven shaft arranged in the vertical direction, and performs reciprocating linear motion and inconstant speed rotational motion with the driven shaft (for example, the upper part is opened), and the object to be stirred is accommodated A bowl-shaped container;
When the bowl-shaped container performs reciprocating linear motion and inconstant speed rotational motion, a stirring body such as a spatula that stirs the stirring target object at least temporarily in contact with the inner surface thereof;
It is characterized by providing.

  According to such a stirrer, when the bowl-shaped container performs a reciprocating linear motion and an inconstant speed rotation movement, the stirring target object such as a powder (dry type) or slurry (wet type) in the bowl-shaped container is obtained. It becomes easy to mix by changing the rotational speed of the bowl-like container (change in the combined angular speed), and the stirring object can be uniformly mixed and stirred in a relatively short time. Therefore, a small, compact and inexpensive stirring device can be obtained.

Example 1
Next, embodiments of the present invention will be described with reference to examples shown in the drawings. FIG. 1 is a front partial sectional view showing an example of a grinding apparatus using a power transmission device according to the present invention, FIG. 2 is a right side partial sectional view thereof, and FIG. 3 is a plan view thereof. As shown in FIG. 2, the crushing device 2 includes a power transmission device 1 having a reciprocating slider crank mechanism 10 and a rotation transmission mechanism 20, an electric motor 30 (rotation drive source) that drives the power transmission device 1, and Ceramic mortar 40 (a bowl-like container) made of alumina or the like for accommodating the object to be crushed (crushed object), and ceramic pestle 50 (a crushed object) made of alumina or the like for crushing the object to be crushed into pieces. And a spatula 60 (stirring body) made of rubber or plastic such as silicon that stirs the fragments, and a main body casing 90 (main body portion) that houses the power transmission device 1, the electric motor 30, and the like.

  The main body casing 90 is formed in a box shape by covering the upper and lower openings of the rectangular tubular side wall 90a with a bottom wall 90b and a top plate 90c that are partially opened. In the middle of the main body casing 90, a base plate 92 extends horizontally from the lower surface of the top plate 90c via a plurality of (for example, four) connecting pipes 91 and screws 91a (fixing members; see FIG. 3). It is suspended and fixed. The electric motor 30 is fixed and held on the lower surface side of the base plate 92, while the power transmission device 1 is mounted and fixed on the upper surface side.

  The reciprocating slider crank mechanism 10 of the power transmission device 1 includes an eccentric rotating portion 11 corresponding to a crank of a piston engine, a slide moving portion 14 corresponding to a piston, and a connecting arm 17 (swinging connecting portion) corresponding to a connecting rod. It is comprised including. Specifically, the eccentric rotating part 11 has an eccentric cam 12 (crank arm) that moves at a constant speed (rotation radius r) away from the axis O1 of the motor shaft 31 (drive shaft), and rotates at a constant speed. The motor shaft 31 is disposed (axially supported) in a vertical direction on a bearing case 11 a fixed to the upper surface of the base plate 92 and protrudes upward. The slide moving unit 14 has a stroke s (s = s = s) along a horizontal straight line formed by the slide shaft 15a and the slide bush 15b and orthogonal to the axis O1 of the motor shaft 31 (that is, on the reciprocating linear motion locus K). 2r) has a slider 15 that reciprocates. Further, the connecting arm 17 reciprocally swings around the support shaft 16 of the slider 15 by rotatably supporting the support shaft 13 of the eccentric cam 12 and the support shaft 16 of the slider 15 in a mutually parallel manner. While reciprocating linearly moving with the slide moving unit 14.

  On the other hand, the rotation transmission mechanism 20 of the power transmission device 1 includes a driving shaft 21 that is integrated with the support shaft 13 of the eccentric cam 12 and is rotatably supported by the connecting arm 17 in a form in which the axis O2 is shared. 21 has a driven shaft 23 that is rotatably supported by the connecting arm 17 in a form that is parallel to the shaft 21 and concentrically with the support shaft 16 of the slider 15 and that shares the axis O3. The rotation transmission mechanism 20 is a gear transmission mechanism in which a driving small gear 22 (driving gear) fixed to a driving shaft 21 and a driven large gear 24 (driven gear) fixed to a driven shaft 23 are meshed. It consists of As a result, the driving shaft 21 performs a constant speed rotating motion around the motor shaft 31 at the same period as the eccentric cam 12 of the eccentric rotating portion 11, and the constant speed rotating motion is transmitted from the driving shaft 21 to the driven shaft 23.

  Therefore, the driven shaft 23 of the power transmission device 1 performs a reciprocating linear motion on the reciprocating linear motion locus K in plan view or an extension thereof (see FIG. 3) together with the slide moving unit 14 and the connecting arm 17. Further, the driven shaft 23 includes the rotational angular velocity of the constant speed rotational motion transmitted from the driving shaft 21 via the gear transmission mechanism 20 (the driving side small gear 22 and the driven side large gear 24), and the support shaft 16 ( A non-uniform rotational motion having a combined angular velocity obtained by combining the swing angular velocity based on the reciprocating swing motion of the articulated arm 17 about the axis O3) is performed.

  Next, such reciprocating linear motion and inconstant speed rotational motion of the driven shaft 23 will be described in detail with reference to the operation explanatory plan views of FIGS. 4 and 5 and the graphs of FIGS. 6 and 7. FIG.

(1) Reciprocating linear motion of the driven shaft 23 As already described, the driven shaft 23 performs the reciprocating linear motion with the stroke s on the reciprocating linear motion trajectory K or on its extension together with the slide moving unit 14 and the connecting arm 17. . Specifically, a reciprocating linear motion that reciprocates once every time the driving shaft 21 (motor shaft 31) makes one rotation (one cycle) is performed. For example, from the position in FIG. 4A where the driven shaft 23 (slider 15) is closest to the motor shaft 31 due to the rotation of the driving shaft 21 (near dead center position P1: corresponding to the bottom dead center of the piston engine), the driven shaft 5 returns to the near dead center position P1 of FIG. 4A again after passing through the position of FIG. 5A farthest from the motor shaft 31 (far dead center position P4: corresponding to the top dead center of the piston engine). At this time, as shown in FIG. 6, the moving speed of the driven shaft 23 (support shaft 16 of the slider 15) is unequal with respect to the rotation angle of the drive shaft 21 (support shaft 13 of the eccentric cam 12). Fast linear motion). In FIG. 6, the movement from the near dead center position P1 (rotation angle 0 °; FIG. 4A) to the far dead center position P4 (rotation angle 180 °; FIG. 5A) is positive, far dead center. The movement from the position (rotation angle 180 °) to the near dead center position P1 (rotation angle 360 °; FIG. 4A) is represented by a negative value. 1 to 3 show the case where the driving shaft 21 (the support shaft 13 of the eccentric cam 12) is at the far dead center position P4 (FIG. 5A).

(2) Unequal speed rotation motion of the driven shaft 23 As already described, the driven shaft 23 has the rotational angular velocity (FIG. 7A) of the constant speed rotation motion transmitted from the drive shaft 21 and the reciprocation of the connecting arm 17. An inconstant speed rotary motion having a combined angular velocity (FIG. 7C) with a swing angular velocity (FIG. 7B) based on the swing motion is performed.

(2-1) Speed increase region (first swing range A1)
As the articulated arm 17 swings, the driving shaft 21 (the support shaft 13 of the eccentric cam 12) moves away from the one swing limit position P3 (the rotation angle α of the driving shaft 21) shown in FIG. Between P4 (FIG. 5A) and reaching the other swing limit position P5 (rotation angle β of the drive shaft 21) shown in FIG. 5B (however, 90 ° <α <180 °; β = 360 ° −α), the swinging motion direction (clockwise) of the connecting arm 17 is the rotational motion direction of the driven shaft 23 transmitted from the driving shaft 21 via the driving side small gear 22 and the driven side large gear 24. (Clockwise) matches (forward direction) (FIG. 5A). Accordingly, during P3 (FIG. 4C) -P4 (FIG. 5A) -P5 (FIG. 5B) (first swing range A1), the driven shaft shown in FIG. The combined angular velocity 23 is increased by a value obtained by adding the angular velocity of the connected arm 17 shown in FIG. 7 (b) to the rotational angular velocity of the constant speed rotation of the driven shaft 23 shown in FIG. 7 (a). The

(2-2) Deceleration region (second swing range A2)
On the other hand, the driving shaft 21 (the support shaft 13 of the eccentric cam 12) moves from the other swing limit position P5 (the rotation angle β of the driving shaft 21) shown in FIG. Between the a)) and the one swing limit position P3 (rotation angle α of the drive shaft 21) shown in FIG. 4C, the swing movement direction (counterclockwise) of the connecting arm 17 is The direction of rotation of the driven shaft 23 (clockwise) is opposite (reverse direction) (FIGS. 5C, 4A, and 4B). Therefore, between P5 (FIG. 5 (b))-P6 (FIG. 5 (c))-P1 (FIG. 4 (a))-P2 (FIG. 4 (b)) (second swing range A2), The combined angular velocity of the driven shaft 23 shown in FIG. 7C is obtained from the rotational angular velocity of the constant-speed rotational motion of the driven shaft 23 shown in FIG. 7A from the swing angular velocity of the connecting arm 17 shown in FIG. Decrease the absolute value.

(2-3) Inversion area (A3)
Further, in the second swing range A2 (deceleration region), the swing of the connecting arm 17 shown in FIG. 7B is larger than the rotational angular velocity of the constant speed rotary motion of the driven shaft 23 shown in FIG. A region (inversion region A3) where the absolute value of the angular velocity is larger is included. Therefore, from the reversal start position P7 (rotation angle 360 ° −θ of the drive shaft 21) to the reversal end position P8 (rotation angle θ of the drive shaft 21) across the near dead center position P1 (FIG. 4A). In the meantime (inversion area A3), the combined angular velocity of the driven shaft 23 shown in FIG. 7C changes negatively (inversion = reverse rotation). When the gear ratio between the driving small gear 22 and the driven large gear 24 is increased, the angular speed of the driven large gear 24 is relatively increased, so that the width (area) of the reversal region A3 tends to decrease. . In order to ensure an appropriate width (area) of the reversal region A3, the gear ratio between the driving side small gear 22 and the driven side large gear 24 is within a range of 1: 2 to 1:10 (for example, 1: 4). Is desirable.

  As described above, the driven shaft 23 of the power transmission device 1 simultaneously performs the reciprocating linear motion (non-uniform linear motion) and the non-uniform rotational motion. As a result, a rotational speed change (change in the combined angular speed) is imparted to the mortar 40 (see FIG. 2) fixed to the driven shaft 23, and the material to be pulverized easily mixes, and the powder form is fine and uniform in a relatively short time. Can be broken into pieces.

  The power transmission device 1 and the electric motor 30 are fixed to a base plate 92 that is suspended and held on the top plate 90c of the main body casing 90, and are not attached to the bottom wall 90b. As a result, the assembling accuracy can be improved, the assembling cost (man-hours) can be reduced, and vibration and noise can be prevented.

  Returning to FIG. 1, the mortar 40 is placed on the upper end portion of the driven shaft 23 in a form in which the axis line O <b> 3 is made common via the mortar placement table 41. Then, the upper surface of the mortar 40 and the lower surface of the mortar mounting table 41 are sandwiched by a plurality of stoppers 42 arranged in the circumferential direction (for example, three at equal intervals; see FIG. 3), and are fastened and fixed by a fixing member 43 such as a knob screw. Has been.

  As shown in FIG. 2, the pestle 50 always contacts (presses) the inner surface of the mortar 40 when the mortar 40 performs reciprocating linear motion (non-uniform linear motion) and non-uniform rotational motion simultaneously. Crush and crush into pieces. The pestle 50 (the axis thereof) is fixedly disposed on the main body casing 90 (main body portion) so as to be positioned on or along the reciprocating linear motion locus K of the axis O3 (see FIG. 1) of the driven shaft 23 in FIG. ing. Specifically, the elevating shaft 94 is inserted vertically through the top plate 90c and the bracket 93 fixed to the upper surface thereof, and the tip of the fixed arm 95 extending horizontally from the upper end of the elevating shaft 94, A pestle 50 is attached via a bush (not shown) with a ball so that it can be moved up and down and rotated. In FIG. 2 again, the pestle 50 is always pressed and held downward on the inner surface of the mortar 40 by the pressing force and weight of the compression coil spring 96 (pressing member) interposed between the fixed arm 95 and the pestle 50. Yes.

  With the above configuration, the relative movement stroke s of the pestle 50 with respect to the mortar 40 can be increased to the full inner diameter of the mortar 40. Further, since the inner bottom surface of the mortar 40 and the outer peripheral surface of the lower end portion of the pestle 50 are each formed in a hemispherical shape, even if the lower end portion of the pestle 50 is always in contact (pressed) with the inner surface of the mortar 40, the mortar 40 The reciprocating linear motion and the non-uniform speed rotational motion can be smoothly performed.

  The upper end portion of the rod-shaped member 94 a is fixed to the lower end portion of the elevating shaft 94, and the lower end portion of the rod-shaped member 94 a is inserted into a guide member 94 b extending from the base plate 92. A compression coil spring 94c (elastic member) is interposed between the lower end surface of the elevating shaft 94 and the upper surface of the guide member 94b. Therefore, when the fixing lever 93a for fixing the elevating shaft 94 to the bracket 93 is loosened, the elevating shaft 94, the fixing arm 95, the pestle 50, the spatula 60, etc. are lifted upward and held together by the elastic force of the compression coil spring 94c. (Imaginary line in FIG. 2) can be made, so that the mortar 40 can be easily attached and detached. Reference numeral 97 denotes a manual switch for turning on / off the drive of the electric motor 30.

  Next, the specific shape of the spatula 60 is shown in FIG. The spatula 60 is made of rubber or plastic, such as silicon, and has a substantially right-angled triangular spatula body 61 in a form in which two sides sandwiching a right angle are directed in the vertical direction and the horizontal direction, respectively, through a plate-like mounting member 63. It is fixed to the mounting member 62.

  Further, as shown in FIG. 3, the spatula 60 is positioned in the vicinity of the pestle 50 and fixedly disposed on the main body casing 90. When the mortar 40 performs the reciprocating linear motion and the inconstant speed rotational motion, At least temporarily contact and stir the crushed pieces with the pestle 50. Specifically, the distal end portion of the fixing arm 95 to which the pestle 50 is attached is bent and formed in an L shape in plan view, and the rod-like attachment member 62 of the spatula 60 is inserted into the bent portion to fix the fixing member such as a knob screw. Fastened and fixed at 95a (see FIG. 1).

The positioning of the spatula 60 by the knob screw 95a and the stirring action by the spatula 60 are performed as shown in FIG.
(1) First, as shown in FIG. 9A, the driving shaft 21 is at the near dead center position P1 (rotation angle 0 °; see FIG. 4A), and the mortar 40 is closest to the lifting shaft 94. In the stopped state, the spatula body 61 is fastened and fixed with a knob screw 95a (see FIG. 1) so that the tip of the spatula body 61 comes into light contact with the inner wall of the mortar 40 and receives the object to be crushed or debris.
(2) Speed increase region [P3 (FIG. 4 (c))-P4 (FIG. 5 (a))-P5 (FIG. 5) in the inequality rotational motion of the mortar 40 by the rotation of the electric motor 30 (see FIG. 2). (B))], in particular, as shown in FIG. 9C, when the driving shaft 21 is at the far dead center position P4 (rotation angle 180 °; see FIG. 5A), the spatula body 61 The tip of the mortar is located between the pestle 50 and the wall of the mortar 40 that are close to each other and is in contact with the wall of the mortar 40 over a wide range. Have the effect of guiding.

  At this time, the object to be crushed is crushed at the highest speed and efficiently by the grinding of the pestle 50 and the mortar 40 in the speed increasing region (for example, FIG. 9 (c) [see FIG. 5 (a)]). The crushed pieces are received by the spatula 60 and guided (returned) to the center of the mortar 40, so that the crushing action and the stirring action can be efficiently performed. Thereafter, the debris is decelerated rotation of the mortar 40 (deceleration region or reversal region; for example, FIG. 9B, FIG. 9A [see FIG. 5C, FIG. 4A, FIG. 4B]). Therefore, the crushing action and the stirring action in the next cycle can be exerted smoothly. By the way, when the crushing apparatus 2 is used for a wet type that crushes and mixes particularly into slurry-like pieces, slurry pieces after crushing that easily adhere along the inner surface of the wall of the mortar 40 by the spatula 60 are removed. It can be scraped off to the inner bottom side of the mortar 40. In FIG. 9B, the driving shaft 21 (support shaft 13 of the eccentric cam 12) is in the intermediate position P2 (rotation angle 90 °; see FIG. 4B) or intermediate position P6 (rotation angle 270 °; FIG. 5). (See (c)).

  Incidentally, as described above, the driven shaft 23 and the mortar 40 of the crushing device 2 shown in FIG. 3 simultaneously perform the reciprocating linear motion (inconstant linear motion) and the inconstant rotational motion. In contrast, the pestle 50 and the spatula 60 are located inside the mortar 40 and are fixed to the main body casing 90. As a result, the pestle 50 and the spatula 60 move relative to the mortar 40 while drawing the number “8” in a plan view every cycle (one rotation) of the driving shaft 21 (motor shaft 31). .

  As shown in FIG. 1 to FIG. 3, a transparent plastic (for example, acrylic) on the lower surface of the fixed arm 95 that is wider than the outer diameter of the mortar 40 and has an elongated oval or oval shape along the reciprocating movement direction K. A lid 98 made of metal is attached so as to cover the moving range of the mortar 40 horizontally. On the other hand, a peripheral wall 99 made of plastic (for example, vinyl chloride) is attached and fixed to the mortar 40 (stopper 42) so as to extend along the outer periphery of the mortar 40 to the lower surface proximity position or contact position of the lid 98. . The lid 98 and the peripheral wall 99 prevent the object to be crushed and its fragments from jumping upward (outside) from the mortar 40 or blowing out. In order to bring the lid 98 closer to the mortar 40 side, the peripheral wall 99 may be omitted if it is provided below the compression coil spring 96 as indicated by a virtual line in FIG. 1 or FIG. In addition, a circular lid is directly put on and fixed to the upper surface of the mortar 40, and a groove for avoiding interference due to the relative movement between the mortar 40 (moving side) and the pestle 50 and spatula 60 (fixing side) is passed through the lid. It may be formed.

(Example 2)
FIG. 10 shows an example of a stirring device using the power transmission device according to the present invention. This stirring device 3 corresponds to the crushing device 2 shown in Example 1 (FIG. 1) except for the pestle 50 (crushed body) and the members associated therewith. Therefore, the rotational speed change (change in the combined angular speed) is imparted to the bowl-shaped container 40 fixed to the driven shaft 23 so that the material to be stirred can be easily mixed and can be uniformly mixed and stirred in a relatively short time. In addition, in Example 2 (FIG. 10), the part which has the function which is common in Example 1 (FIGS. 1-9) is attached | subjected, and description is abbreviate | omitted.

(Example of change)
Next, the schematic structure and operation of the power transmission device shown in FIGS. 11 and 12 will be described. The power transmission device 100 is modified as follows from the power transmission device 1 shown in the first embodiment (FIGS. 4 and 5).
(1) An offset crank mechanism 110 is used in place of the reciprocating slider crank mechanism 10. That is, the reciprocating linear motion locus K of the slider 15 (support shaft 16) or its extension does not intersect the motor shaft 31 (axis O1).
(2) Although the drive shaft 21 is integrated with the support shaft 13 of the eccentric cam 12, the drive shaft 21 (drive side small gear 22) and the driven shaft 23 (driven side large) of the gear transmission mechanism 120 (rotation transmission mechanism). An intermediate shaft 121 (intermediate gear 122) is interposed between the gear 24).
(3) The driven shaft 23 (axis line O3) is not concentric with the support shaft 16 of the slider 15, but is in a different position.

  Accordingly, the driven shaft 23 of the power transmission device 100 performs a reciprocating linear motion in parallel with the reciprocating linear motion locus K of the slider 15 together with the slide moving unit 14 and the connecting arm 17. Further, the driven shaft 23 includes a rotational angular velocity of a constant rotational motion transmitted from the driving shaft 21 via the gear transmission mechanism 120 (the driving side small gear 22, the intermediate gear 122 and the driven side large gear 24), and the slider 15. An inconstant speed rotational motion having a combined angular velocity obtained by combining the swing angular velocity based on the reciprocating swing motion of the connecting arm 17 around the support shaft 16 is performed.

  Next, the reciprocating linear motion and the inconstant speed rotational motion of the driven shaft 23 will be schematically described with reference to the operation explanatory plan views of FIGS. 11 and 12.

(1) Reciprocating linear motion of the driven shaft 23 The driven shaft 23 performs the reciprocating linear motion with the stroke s in parallel with the reciprocating linear motion locus K together with the slide moving unit 14 and the connecting arm 17. Specifically, a reciprocating linear motion that reciprocates once every time the driving shaft 21 (motor shaft 31) makes one rotation (one cycle) is performed. For example, from the position in FIG. 11A where the driven shaft 23 (slider 15) is closest to the motor shaft 31 by the rotation of the driving shaft 21 (near dead center position P1: corresponding to the bottom dead center of the piston engine), the driven shaft 12 returns to the near dead center position P1 in FIG. 11 (a) again after passing through the position shown in FIG. 12 (a) farthest from the motor shaft 31 (far dead center position P4: corresponding to the top dead center of the piston engine).

(2) Inconstant speed rotational motion of the driven shaft 23 The driven shaft 23 is a combined angular velocity of the rotational angular velocity of the constant speed rotational motion transmitted from the driving shaft 21 and the swing angular velocity based on the reciprocating swing motion of the connecting arm 17. An inconstant speed rotational movement is performed.

(2-1) Deceleration region (second swing range A2)
As the articulated arm 17 swings, the driving shaft 21 (the support shaft 13 of the eccentric cam 12) moves from the one swing limit position P3 (the rotation angle α of the driving shaft 21) shown in FIG. Between P4 (FIG. 12 (a)) and reaching the other swing limit position P5 (rotation angle β of the drive shaft 21) shown in FIG. 12 (b) (where 90 ° <α <180 °; 180 In the case of ° <β <270 °, the swinging motion direction (clockwise) of the connecting arm 17 is the driven shaft transmitted from the driving shaft 21 via the driving side small gear 22, the intermediate gear 122, and the driven side large gear 24. It is opposite (reverse direction) to the rotational movement direction (counterclockwise) of 23 (FIG. 12 (a)). Accordingly, during P3 (FIG. 11 (c))-P4 (FIG. 12 (a))-P5 (FIG. 12 (b)) (second swing range A2), the combined angular velocity of the driven shaft 23 is the driven The speed is reduced to a value obtained by subtracting the absolute value of the swing angular velocity of the articulated arm 17 from the rotational angular velocity of the constant-speed rotational motion of the shaft 23.

(2-2) Speed increase region (first swing range A1)
On the other hand, the drive shaft 21 (the support shaft 13 of the eccentric cam 12) moves from the other swing limit position P5 (the rotation angle β of the drive shaft 21) shown in FIG. During the period between the swing limit position P3 (rotation angle α of the drive shaft 21) shown in FIG. 11 (c) across the a)), the swing movement direction (counterclockwise) of the connecting arm 17 is It coincides (forward direction) with the rotational movement direction (counterclockwise) of the driven shaft 23 (FIG. 12C, FIG. 11A, FIG. 11B). Therefore, between P5 (FIG. 12 (b))-P6 (FIG. 12 (c))-P1 (FIG. 11 (a))-P2 (FIG. 11 (b)) (first swing range A1), The combined angular velocity of the driven shaft 23 is increased to a value obtained by adding the swing angular velocity of the articulated arm 17 to the rotational angular velocity of the constant speed rotational motion of the driven shaft 23.

(2-3) Inversion area (A3)
Further, in the second swing range A2 (deceleration region), a region where the absolute value of the swing angular velocity of the articulated arm 17 is larger than the rotational angular velocity of the constant speed rotation of the driven shaft 23 (reversal region). A3) is included.

  As described above, the driven shaft 23 of the power transmission device 100 simultaneously performs the reciprocating linear motion (non-uniform linear motion) and the non-uniform rotational motion. As a result, a rotational speed change (change in the combined angular speed) is imparted to the mortar 40 (see FIG. 2) fixed to the driven shaft 23, and the material to be pulverized easily mixes, and the powder form is fine and uniform in a relatively short time. Can be broken into pieces. Since the intermediate gear 122 is interposed in the gear transmission mechanism 120 of the power transmission device 100, the positional relationship between the speed increasing area and the speed reducing area is opposite to that in the first embodiment.

  In the above description, a dry crushing apparatus for crushing and mixing powdery debris and a dry stirrer for mixing and stirring powdery substances are described. You may use for the wet crushing apparatus for mixing, and the wet stirring apparatus for mixing and stirring a slurry-like substance uniformly. Further, although the pestle 50 and the spatula 60 are fixed to the main body casing 90, they may be driven by an electric motor or the like (for example, in-situ rotation around the axis). Furthermore, a plurality of pestles 50 and spatulas 60 may be arranged for a single mortar 40. And although the rotation transmission mechanisms 20 and 120 were comprised with the gear transmission mechanism, you may comprise with winding transmission mechanisms, such as a V belt.

  In the embodiment, only the case where the power transmission device according to the present invention is used in the crushing device and the stirring device has been described, but the power transmission device of the present invention is not limited to these applications. For example, the present invention can also be applied to a vibrating sieve device, a shaking device such as a test tube, a beaker, or a flask.

The front fragmentary sectional view which shows an example of the crushing apparatus using the power transmission device which concerns on this invention. FIG. 2 is a right side partial cross-sectional view of FIG. 1. The top view of FIG. The top view explaining the action | operation of a power transmission device. The top view explaining the action | operation of a power transmission device following FIG. The graph showing the change of the moving speed of a driven shaft based on the action | operation of FIG.4 and FIG.5. The graph showing the change of the angular velocity of a driven shaft based on the action | operation of FIG.4 and FIG.5. The front view and right view of the stirring spatula with which the crushing apparatus of FIG. 1 is mounted | worn. The top view explaining the effect | action of the spatula for stirring of FIG. The front fragmentary sectional view which shows an example of the stirring apparatus using the power transmission device which concerns on this invention. FIG. 6 is a plan view for explaining the schematic structure and operation of a power transmission device in place of FIG. 4 and FIG. 5. The top view explaining the schematic structure and operation | movement of a power transmission device following FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Power transmission device 2 Crushing device 3 Agitation device 10 Reciprocating slider crank mechanism 11 Eccentric rotation part 12 Eccentric cam (crank arm)
13 Eccentric cam support shaft (crank arm support shaft)
14 Slide moving part 15 Slider 16 Slider support shaft 17 Connecting arm (oscillating connecting part)
20 Gear transmission mechanism (Rotation transmission mechanism)
21 Drive shaft 22 Drive side small gear (drive gear)
23 driven shaft 24 driven large gear (driven gear)
30 Electric motor (rotation drive source)
31 Motor shaft (drive shaft)
40 Mortar (boiled container)
50 pestle (crushed body)
60 spatula (stirring body)
90 Main body casing (main body)
DESCRIPTION OF SYMBOLS 100 Power transmission device 110 Offset crank mechanism 120 Gear transmission mechanism (rotation transmission mechanism)
121 Intermediate shaft 122 Intermediate gear A1 Speed increase area (first swing range)
A2 Deceleration area (second swing range)
A3 Reverse area K Reciprocal linear motion locus O1 Motor axis (drive axis)
O2 Drive axis O3 Drive axis

Claims (9)

An eccentric rotating part in which the crank arm rotates away from the drive shaft by a predetermined distance, a slide moving part in which the slider reciprocates on a straight line, a support shaft of the crank arm, and a support shaft of the slider are respectively rotatable. A reciprocating slider crank mechanism or an offset crank mechanism, each having a reciprocating linearly reciprocating motion with the slide moving portion while reciprocatingly reciprocatingly swinging around a support shaft of the slider,
A driving shaft that is rotatably supported by the oscillating connecting portion, and that rotates around the drive shaft in synchronization with the rotating motion of the crank arm of the eccentric rotating portion, and is arranged in parallel with the driving shaft; A rotation shaft that is rotatably supported by the oscillating joint, and a rotational transmission mechanism that transmits rotational motion from the driving shaft to the driven shaft;
With
The driven shaft performs a reciprocating linear motion together with the slide moving portion and the oscillating connecting portion, and the rotational angular velocity of the rotational motion transmitted from the driving shaft via the rotational transmission mechanism and the support shaft of the slider are centered. A power transmission device that performs an inconstant rotational motion having a combined angular velocity obtained by combining a swing angular velocity based on a reciprocating swing motion of the swing connecting portion. An eccentric rotating part in which the crank arm rotates at a constant speed away from the drive shaft at a constant speed, a slide moving part in which the slider reciprocates on a straight line perpendicular to the axis of the drive shaft, a support shaft of the crank arm, and the A reciprocating reciprocating portion having a support shaft of the slider rotatably and parallel to each other, and a reciprocating reciprocating motion about the support shaft of the slider and a reciprocating linear motion together with the slide moving portion. A slider crank mechanism;
It is integrated with the support shaft of the crank arm that is rotatably supported by the rocking connecting portion, and performs constant speed rotation around the drive shaft at the same period as the constant speed rotation of the crank arm of the eccentric rotation portion. The drive shaft is arranged in parallel with the drive shaft and concentrically with the support shaft of the slider rotatably supported by the swing connecting portion, and is rotatably supported by the swing connecting portion. A rotation transmission mechanism that transmits a constant speed rotation motion from the driving shaft to the driven shaft,
With
While the driven shaft performs a reciprocating linear motion that reciprocates once every cycle in which the driving shaft rotates once, together with the slide moving portion and the swing connecting portion,
(1) In the cycle, the rotational motion of the driven shaft is transmitted from the driving shaft via the rotational transmission mechanism in the direction of the swinging motion of the swinging connecting portion around the support shaft of the slider. In the first swing range that is the same direction as the direction, the rotational angular velocity of the constant speed rotational motion transmitted from the driving shaft is combined with the swing angular velocity based on the reciprocal swing motion of the swing joint. To perform a non-uniform rotational motion with an increased combined angular velocity,
(2) Of the one cycle, in the second swing range in which the swing motion direction of the swing joint is opposite to the rotational motion direction of the driven shaft, the rotational angular velocity of the constant speed rotational motion is A power transmission device that performs non-uniform speed rotation motion having a combined angular velocity that is decelerated by being combined with a swing angular velocity based on the reciprocating swing motion.   In the second swing range, a reversal region in which the combined angular velocity of the driven shaft is reversed positively and negatively when a swing angular velocity based on the reciprocating swing motion exceeds a rotational angular velocity of the constant speed rotary motion is partially provided. The power transmission device according to claim 2 including.   4. The rotation transmission mechanism is constituted by a gear transmission mechanism in which a driving side small gear fixed to the driving shaft and a driven side large gear fixed to the driven shaft are meshed with each other. The power transmission device according to claim 1. The power transmission device according to any one of claims 1 to 4,
A rotational drive source such as an electric motor that rotationally drives the drive shaft disposed in the vertical direction;
A bowl in which the object to be crushed is contained like a mortar, which is placed and fixed on the upper end portion of the driven shaft arranged in the vertical direction and performs the reciprocating linear motion and the non-uniform rotation motion with the driven shaft. A container,
When the bowl-like container performs the reciprocating linear movement and the inconstant speed rotation movement, it is at least temporarily in contact with the inner surface of the bowl-like container to crush and crush the object to be crushed into pieces. Body,
A crushing device characterized by comprising:   The crushed body is in a reciprocating straight line of the axis of the driven shaft in a plan view so that the bowl-shaped container always contacts the inner surface of the bowl-shaped container while performing the reciprocating linear motion and the non-uniform rotational motion. The crushing device according to claim 5, wherein the crushing device is fixedly disposed on the main body portion and pressed and held downward so as to be positioned on the movement locus or on an extension thereof.   When the bowl-shaped container performs the reciprocating linear movement and the inconstant speed rotation movement, it is at least temporarily in contact with the inner surface of the bowl-shaped container and agitates the debris of the ground object that has been ground by the ground body. Therefore, the crushing apparatus according to claim 5 or 6, wherein a stirring body such as a spatula is disposed in the vicinity of the crushing body.   The stirrer is in a speed increasing region in the inconstant speed rotational movement of the bowl-shaped container, and is between the crushing body and the wall of the bowl-shaped container that are close to each other and is in contact with the wall of the bowl-shaped container The crushing apparatus according to claim 7, wherein the crushing object is crushed by the crushing object and is guided toward the center of the bowl-shaped container. The power transmission device according to any one of claims 1 to 4,
A rotational drive source such as an electric motor that rotationally drives the drive shaft disposed in the vertical direction;
A bowl-shaped container containing a stirring object, which is placed and fixed on the upper end portion of the driven shaft arranged in the vertical direction, and performs the reciprocating linear motion and the non-uniform rotation motion with the driven shaft;
When the bowl-shaped container performs the reciprocating linear motion and the inconstant speed rotational motion, a stirring body such as a spatula that stirs the stirring target object at least temporarily in contact with the inner surface thereof;
A stirrer comprising:

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