JP2010209903A - Rotary cam type reciprocating object and pump using the same - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a driving force transmission technique which can convert the rotation movement to the linear reciprocal movement while the rotary cam is always contact with the circumferential surface due to the rotary cam comprising the eccentric cam and the planetary cam in combination. <P>SOLUTION: A drive shaft is disposed in a direction orthogonal to the reciprocal movement of the reciprocating object. On this drive shaft, the eccentric cam is mounted. Further, the planetary cam is eccentrically out-fitted with the eccentric cam. The eccentric cam and the planetary cam constitute the rotary cam. The rotary cam is fitted in the cam hole of the reciprocating object. When the drive shaft is rotated, the eccentric cam repeatedly moves the reciprocating object in the horizontal direction by the eccentricity quantity thereof. Further, the planetary cam repeatedly moves the reciprocating object in the horizontal direction by the eccentricity quantity thereof corresponding to the rotation of the eccentric cam. The rotation movement of the drive shaft is converted to the linear reciprocal movement of the reciprocating object through the surface-joint part of cylindrical outer peripheral surfaces of the eccentric cam and the planetary cam. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotary cam in which a moving body is linearly reciprocated by a rotary cam comprising an eccentric cam fixed to a drive shaft and a planetary cam eccentrically fitted to the outer peripheral surface of the eccentric cam. TECHNICAL FIELD The present invention relates to a reciprocating moving body and a pump technology using the same.

  Conventionally, a piston mechanism as a moving body that reciprocates linearly is used in a refrigerant compressor, a vacuum pump, a plunger pump, or the like of a compressor that sucks / pumps fluid. Generally, a connecting rod is connected to a crankshaft or a camshaft, a piston is attached to the tip of the connecting rod, and the piston is reciprocated linearly in a container such as a housing, a casing, or a cylinder. Then, a valve body is attached to a space whose volume changes due to the reciprocating movement of the piston, and the fluid is sucked / pumped.

  However, in the method using the connecting rod, in addition to the stroke of the piston, the housing and the casing increase in size by the length of the connecting rod, and the reciprocating movement of the piston comes into contact with the inner wall of the cylinder, etc. There was a drawback that the wear on the piston and cylinder side became severe. Further, the piston and the connecting rod are connected so as to be swingable by inserting a piston pin. However, since the piston pin is thin, there is a problem that it is easily broken.

  As a means for solving such a problem, the eccentric cam driving technique shown in Patent Document 1 and Patent Document 2 has already been developed. In these techniques of Patent Documents 1 and 2, an eccentric cam is attached to a drive shaft, and a long elliptical window in which the eccentric cam is joined to the inner peripheral surface is provided on a member that supports a piston. When the drive shaft is rotated, the eccentric cam rotates eccentrically so as to push the piston while moving up and down the inner peripheral surface of the long window, and the piston support and the piston at the tip thereof are reciprocated.

JP 2003-172263 A Japanese Utility Model Publication No. 54-140312

  However, in the techniques of Patent Documents 1 and 2, when the eccentric cam is joined to the linear portion of the long window, it is in a line contact state, and the load of the driving force is concentrated so that the eccentric cam and the long window The wear of the peripheral surface became severe, causing problems such as piston support and backlash of the piston moving back and forth, loss of driving force, and deterioration of members due to heat generation. For this reason, there have been problems that the life of the eccentric cam and the piston support is short, parts must be replaced in a short period, and maintenance must be frequently performed in a short period.

  The present invention has been improved and removed in view of the above-described conventional problems, and further comprises an eccentric cam attached to a drive shaft to further eccentrically attach a planetary cam to form a rotary cam. By reciprocating a reciprocating body such as a piston, a driving force transmission technique that is always joined on a circumferential surface is provided.

  Thus, the means of claim 1 adopted by the present invention to solve the above-mentioned problem is that the reciprocating body mounted in the casing so as to be reciprocally movable and the reciprocating direction of the reciprocating body are orthogonal. Drive shaft disposed in the direction, an eccentric cam mounted on the drive shaft, a cam hole provided in the reciprocating body and mounted on the outer peripheral surface of the eccentric cam so as to be eccentric and rotatable. A rotary cam type reciprocating body characterized by comprising a planetary cam fitted and mounted to be freely rotatable.

  The means of claim 2 employed by the present invention includes a reciprocating body mounted in a casing so as to be reciprocally movable, a drive shaft disposed in a direction orthogonal to the reciprocating direction of the reciprocating body, An eccentric cam mounted on the drive shaft, and a planetary cam which is eccentrically fitted on the outer peripheral surface of the eccentric cam and is rotatably fitted and mounted in a cam hole provided in the reciprocating body. A pushing force forming portion provided on the back side of the reciprocating body and having an oblong sliding guide surface; and an extrusion mounted eccentrically on the drive shaft and fitted to the pushing force forming portion. It is a rotary cam type reciprocating body characterized by comprising a cam.

  According to the third aspect of the present invention, the drive shaft and the planetary cam are in a concentric positional relationship at the midpoint of the reciprocating stroke, and the eccentric cam is in a positional relationship in which the eccentric cam is eccentric by a predetermined dimension. It is a rotary cam type reciprocating body according to claim 1 or 2.

  According to a fourth aspect of the present invention, there is provided a reciprocating body mounted in a casing so as to be capable of reciprocating movement, a piston attached to a tip side of the reciprocating body, and a reciprocating direction of the reciprocating body. Is a drive shaft disposed in a perpendicular direction, an eccentric cam mounted on the drive shaft, and is eccentrically mounted on the outer peripheral surface of the eccentric cam so as to be rotatably fitted and provided on the reciprocating body. A planetary cam that is rotatably fitted in and attached to the cam hole, a pressure chamber in which the volume ratio is changed by the reciprocating movement of the reciprocating body and the piston in the casing, an inlet and a discharge port formed in the pressure chamber, The pump comprises a reciprocating body and a valve body that automatically opens and closes the inflow port and the discharge port in response to the reciprocating movement of the piston.

  The means of claim 5 employed by the present invention includes a reciprocating body mounted in a casing so as to be capable of reciprocating movement, a piston attached to a front end side of the reciprocating body, and a reciprocating direction of the reciprocating body. Is a drive shaft disposed in a perpendicular direction, an eccentric cam mounted on the drive shaft, and is eccentrically mounted on the outer peripheral surface of the eccentric cam so as to be rotatably fitted and provided on the reciprocating body. A planetary cam that is rotatably fitted in the cam hole, a pushing force forming portion having an oblong slide guide surface on the back side of the reciprocating body, and an eccentric mounting on the drive shaft. An extrusion cam fitted and mounted on the pushing force forming portion, a pressure chamber in which the volume ratio is changed by the reciprocating movement of the reciprocating body and the piston in the casing, an inlet and a discharge port formed in the pressure chamber, , Reciprocating movement of reciprocating body and piston A pump, characterized in that correspondingly configured in the valve body for automatically opening and closing the inlet and discharge ports.

  According to a sixth aspect of the present invention, the drive shaft and the planetary cam are in a concentric positional relationship at an intermediate point of the reciprocating stroke, and the eccentric cam is in a positional relationship in which the eccentric cam is eccentric by a predetermined dimension. The pump according to claim 4 or 5, wherein

  In the invention of claim 1, the reciprocating body is mounted in the casing so as to be reciprocally movable. In this case, the following description will be made assuming that the reciprocating body is mounted so that the vertical movement of the casing is restricted and can be reciprocated in the left-right direction in each drawing. A drive shaft is arranged in a direction perpendicular to the reciprocating direction of the reciprocating body. An eccentric cam is fixedly installed on the drive shaft by key fitting or the like. On the outer peripheral surface of the eccentric cam, a planetary cam is eccentrically fitted and mounted so as to be rotatable. The eccentric cam and the planetary cam constitute a rotary cam. The planetary cam is rotatably fitted in a cam hole provided in the reciprocating body.

  When the drive shaft is rotated, the eccentric cam is eccentrically attached to the drive shaft, so that the center OH of the eccentric cam performs a circular motion around the center O of the drive shaft. Assuming that the intersection point of the perpendicular line extending from the center OH of the eccentric cam to the horizontal line H passing through the center O of the drive shaft is X (not shown), this X repeatedly increases and decreases as the eccentric cam rotates. It becomes like this. The change amount of the dimension OX is transmitted to the reciprocating body through the planetary cam and becomes a change amount for moving the reciprocating body in the left-right direction.

  On the other hand, the planetary cam is eccentrically attached to the eccentric cam, and has a minimum portion and a maximum portion of the planetary cam itself. In addition, the planetary cam is fitted in the cam hole of the reciprocating body to restrain the vertical movement. Therefore, when the eccentric cam rotates, the planetary cam externally fitted to the outer peripheral surface of the planetary cam increases or decreases its thickness by the dimension that the center OH of the eccentric cam moves from the horizontal line H in the vertical direction. The self rotates around the eccentric cam in the direction opposite to the rotation direction of the eccentric cam. The increase / decrease in the wall thickness due to the rotation of the planetary cam is converted into a shift amount for moving the reciprocating moving body in the left-right direction.

As described above, the rotational movements of the eccentric cam and the planetary cam are converted into displacement amounts that each move the reciprocating body in the left-right direction, and are maximized at the positions rotated 90 degrees and 270 degrees, respectively.
In short, according to the first aspect of the present invention, when the drive shaft is rotated, the eccentric cam repeatedly moves the reciprocating body in the left-right direction by the amount of the eccentric dimension. In addition, the planetary cam attached eccentrically with respect to the eccentric cam repeatedly moves the reciprocating movable body in the left-right direction by the amount corresponding to the eccentric dimension corresponding to the rotation of the eccentric cam. . The transmission of the driving force for converting the rotational motion of the drive shaft into the linear reciprocating motion of the reciprocating body is performed through the cylindrical outer peripheral surface of the eccentric cam and the planetary cam. Unlike transmission, there are many advantages such as no wear or heat generation of the drive part, long life of parts, no loss of drive force, and long-term maintenance-free operation.

  In the invention of claim 2, in addition to the invention of claim 1, there is provided a mechanism for giving a large pushing force to the reciprocating moving body when the reciprocating moving body starts moving from the position of the intermediate point. Is. A pushing force forming portion provided on the back side of the reciprocating moving body and having an oblong sliding guide surface is provided, and a pushing cam is fitted to the pushing force forming portion. The push cam is eccentrically mounted on the drive shaft, and is in surface contact with the upper and lower circumferential curved surfaces of the sliding guide surface at the position of the intermediate point of the reciprocating moving body. Therefore, when the drive shaft is rotated, the rotational driving force of the drive shaft is directly transmitted to the reciprocating moving body from the position of this intermediate point via the surface joint portion of the circumferential curved surface, and pushed out with a large force. . After the reciprocating body starts to move, the rotational driving force of the drive shaft is transmitted to the reciprocating body by the rotary cam mechanism according to claim 1.

  Therefore, in the second aspect of the invention, a large pushing force can be obtained by the extrusion forming portion and the pushing cam at the intermediate point position where a large driving force cannot be transmitted by the rotary cam mechanism. Smooth reciprocating movement of the moving body is possible.

  In the invention of claim 3, the drive shaft and the planetary cam are in a concentric positional relationship at an intermediate point of the reciprocating stroke, and the eccentric cam is decentered by a predetermined dimension from the center of the drive shaft. It is trying to become. The stroke for reciprocating the reciprocating body is determined by this eccentric relationship. That is, the setting of the stroke of the reciprocating body can be determined by the eccentric amount of the eccentric cam with respect to the drive shaft and the eccentric amount of the planetary cam with respect to the eccentric cam, and the setting operation is easy.

In the invention of claim 4, a piston is attached to the tip of the reciprocating body of the invention of claim 1, a pressure chamber whose volume ratio is changed by the reciprocating movement of the reciprocating body in the casing and the piston is provided, and this A fluid inlet and outlet are formed in the pressure chamber, and a valve body that automatically opens and closes the inlet and outlet in response to the reciprocating movement of the reciprocating body and the piston is provided.
Therefore, in the invention of claim 4, the fluid can be automatically sucked and discharged in response to the reciprocating movement of the reciprocating body. It can be used as a vacuum pump used in a compressor or the like when the fluid is air, a plunger pump when the fluid is a liquid such as water, or a priming pump for a fire fighting pump.

  In the invention of claim 5, the pump mechanism described in claim 4 is applied to the invention of the reciprocating body of claim 2. The effect is the same as that of Claim 2 and Claim 4.

  In the invention of claim 6, in the invention of the pump of claims 4 and 5, the eccentric relationship of the drive shaft, the eccentric cam, and the planetary cam is determined. The invention of claim 3 Has the same effect.

It is a cross-sectional top view which shows the whole vacuum pump which concerns on one embodiment of this invention. It is a longitudinal section front view showing the whole vacuum pump concerning one embodiment of the present invention. It is a longitudinal section side view showing the whole vacuum pump concerning one embodiment of the present invention. It is a side view showing the whole vacuum pump concerning one embodiment of the present invention. It is a side view of the eccentric cam which concerns on one embodiment of this invention. It is a front view of the eccentric cam which concerns on one embodiment of this invention. It is a rear view of the extrusion formation part which concerns on one embodiment of this invention. It is a front view which shows the valve main body of the vacuum pump which concerns on one embodiment of this invention. It is a front view which shows the intake valve of the vacuum pump which concerns on one embodiment of this invention. It is a front view which shows the exhaust valve of the vacuum pump which concerns on one embodiment of this invention. It is process drawing which shows the cam position of the rotary cam mechanism in the left dead center of the vacuum pump which concerns on one embodiment of this invention, and the intake / exhaust relationship of a pump. It is process drawing which shows the cam position of the rotary cam mechanism in the intermediate point in the case of transfering from the left dead center of the vacuum pump which concerns on one embodiment of this invention to a right dead center, and the intake / exhaust relationship of a pump. It is process drawing which shows the cam position of the rotary cam mechanism in the right dead center of the vacuum pump which concerns on one embodiment of this invention, and the intake / exhaust relationship of a pump. It is process drawing which shows the cam position of the rotary cam mechanism in the intermediate point in the case of shifting to the left dead center from the right dead center of the vacuum pump which concerns on one embodiment of this invention, and the intake / exhaust relationship of a pump.

  Hereinafter, the configuration of the present invention will be described with reference to the drawings based on an embodiment of a vacuum pump. 1 to 3 show the entire vacuum pump 1. FIG. 1 is a horizontal sectional plan view, FIG. 2 is a longitudinal sectional front view, FIG. 3 is a longitudinal sectional side view, and FIG. 4 is a side view. In the following description, the “left / right direction” refers to the left / right direction in FIGS. 1 and 2, and the “up / down direction” refers to the up / down direction in FIGS. 3 and 4.

  As shown in the figure, the vacuum pump 1 includes a drive shaft 3 rotatably supported in a direction orthogonal to the central axis of the cylindrical casing 2, and a rotary cam mechanism 4 on the drive shaft 3. The attached reciprocating body 5, the pistons 6A and 6B attached to the left and right ends of the reciprocating body 5, pressure chambers 7A and 7B whose volume ratio changes due to the reciprocating movement of the pistons 6A and 6B, and pressure And valve bodies 8A and 8B disposed in the chambers 7A and 7B.

  A composite cam body 9 shown in FIGS. 5 and 6 is externally fitted to the drive shaft 3 in the cylindrical casing 2 by a key fitting method. The composite cam body 9 has an eccentric cam 10 formed on the front side and an extrusion cam 11 formed integrally on the back side. The eccentric direction of the eccentric cam 10 and the push cam 11 is set to be the same direction. A planetary cam 13 is eccentrically fitted to the eccentric cam 10 via a bearing 12 and is externally fitted. The planetary cam 13 is fitted in the cam hole 15 of the reciprocating body 5 via a bearing 14. The eccentric cam 10 and the planetary cam 13 constitute a rotary cam mechanism 4, and the rotation of the drive shaft 3 is transmitted to the reciprocating body 5 via the rotary cam mechanism 4.

  Thus, the amount of eccentricity of the eccentric cam 10 with respect to the drive shaft 3 and the amount of eccentricity of the planetary cam 13 with respect to the eccentric cam 10 are the positions of the intermediate points in the left-right direction of the reciprocating moving body 5 (shown in FIGS. 12 and 14). Position). That is, the amount of eccentricity of the eccentric cam 10 with respect to the drive shaft 3 is the dimension between O and OH. The eccentric amount of the eccentric cam 10 is represented as a stroke S1 in FIGS. The eccentric amount of the planetary cam 13 with respect to the eccentric cam 10 is set so that the center O of the drive shaft 3 and the center OP of the planetary cam 13 are concentric at the intermediate point position shown in FIGS. . The eccentric amount of the planetary cam 13 at this time is represented as a stroke S2 in FIGS. The stroke S2 is the same as the stroke S1, which is the amount of eccentricity of the eccentric cam 10 with respect to the drive shaft 3. That is, S1 = S2 is set.

  On the back side of the reciprocating body 5, as shown in FIG. 7, there is provided a pushing force forming portion 17 having an elliptical sliding guide surface 16 disposed so as to be vertically long in the vertical direction. ing. The pushing cam 11 of the composite cam body 9 is fitted and attached to the pushing force forming portion 17. In the figure, reference numeral 18 denotes a horizontally elongated oblong hole formed in the reciprocating body 5. The hole 18 is for preventing the reciprocating body 5 from interfering with the drive shaft 3 when the reciprocating body 5 is reciprocated. That is, the drive shaft 3 is driven to rotate at a position fixed to the casing 2, while the reciprocating body 5 reciprocates in the casing 2 through the rotary cam mechanism 4 in the left-right direction as the drive shaft 3 rotates. This is because it is necessary to prevent the reciprocating body 5 from interfering with the drive shaft 3 because it moves.

Pistons 6 </ b> A and 6 </ b> B are attached to the left and right ends of the reciprocating body 5. The pistons 6A and 6B are slidably fitted into the cylinders 19A and 19B of the casing 2, and a plurality of seal rings are attached to the peripheral side surfaces. Thus, as a result of the reciprocating body 5 being connected and fixed to the pistons 6A and 6B, the reciprocating body 5 is restrained from moving in the vertical direction of the casing 2 and can only reciprocate in the left-right direction. It becomes composition.
Further, caps 20A and 20B, to which valve bodies 8A and 8B are attached, are mounted on the distal ends of the cylinders 19A and 19B. The caps 20A and 20B have an intake chamber 21 formed in the center, and an annular exhaust chamber 22 formed on the outer peripheral side thereof. An intake port 23 that communicates with the intake chamber 21 and an exhaust port 24 that communicates with the exhaust chamber 22 are formed outside the caps 20A and 20B.

  Further, the valve bodies 8A and 8B are a plurality of disc-shaped valve bodies 25 shown in FIG. 8, a disc-like intake valve 26 shown in FIG. 9, and a plurality of radial extensions from the central disc shown in FIG. And an exhaust valve 28 provided with the valve 27. The intake valve 26 is attached to the inner surface side of the valve body 25, and the exhaust valve 28 is attached to the outer surface side. The valve body 25 has a plurality of intake holes (inlet ports) 29 concentrically penetratingly formed at positions closer to the center, and a plurality of exhaust holes (discharge ports) 30 penetratingly formed at positions closer to the outer periphery. Has been. In the intake valve 26, a plurality of exhaust holes (discharge ports) 31 are concentrically formed on the outer peripheral side, and mushroom-shaped valves 32 are formed radially from the outer peripheral side to the inner peripheral side at positions near the center. Notches are formed. A plurality of intake holes (inlet ports) 33 are formed concentrically through the disc-shaped portion of the exhaust valve 28.

  Next, the operation | movement aspect of the vacuum pump 1 comprised as mentioned above is demonstrated with reference to the process drawing of FIG. 11 thru | or FIG. In these process drawings, the center of the drive shaft 3 is denoted by the symbol O, the center of the eccentric cam 10 is denoted by the symbol OH, and the center of the planetary cam 13 is denoted by the symbol OP. A point on the circumference of the eccentric cam 10 farthest from the center O of the drive shaft 3 is A, and B is a point on the circumference of the planetary cam 13 farthest from the center OP of the eccentric cam 10. explain. Further, the stroke of the eccentric cam 10 (the same dimension as the eccentric amount with respect to the drive shaft 3) is S1, and the stroke of the planetary cam 13 (the same dimension as the eccentric amount with respect to the eccentric cam 10) is described as S2.

  For the convenience of description of the intake / exhaust process of the vacuum pump 1, a description will be given from the state shown in FIG. 11 in which the piston 7A is at the left dead center moved to the left most. At the left dead center, the center OH of the eccentric cam 10 is on a horizontal line H passing through the center O of the drive shaft 3 and is moved to the left from the center O of the drive shaft 3 by the stroke S1. The point A of the eccentric cam 10 is located on the horizontal line H on the left side of the center OH. On the other hand, the center OP of the planetary cam 13 is on the horizontal line H moved by the stroke S2 to the left from the center OH of the eccentric cam 10, and the point B of the planetary cam 13 is on the horizontal line H on the left side of the center OP. Is located.

  When the drive shaft 3 is rotated 90 degrees in the clockwise direction from such a state, the eccentric cam 10 attached eccentrically to the drive shaft 3 moves circularly about the center O of the drive shaft 3. Will come to do. Accordingly, the point A on the circumference of the eccentric cam 10 is rotationally moved so as to be positioned above the center O of the drive shaft 3 and on the vertical line V passing through the center O as shown in FIG. . In the rotational operation of the eccentric cam 10, the amount of lateral displacement of the eccentric cam 10 is an X (shown in the figure) where a perpendicular line extending from the center OH of the eccentric cam 10 to the horizontal line H of the drive shaft 3 intersects the horizontal line H. (Omitted) is the distance from the position of the center OH of the eccentric cam 10 on the horizontal line H shown in FIG. The lateral displacement of the eccentric cam 10 is transmitted to the reciprocating body 5 through the planetary cam 13. In the case of rotating from the state of FIG. 11 to the state of FIG. 12, the force is used to move the reciprocating body 5 to the right. Since the reciprocating body 5 is restrained from moving up and down in this direction, the amount of displacement accompanying the rotation of the eccentric cam 10 is converted into the amount of displacement that moves the reciprocating body 5 left and right through the planetary cam 13. It is. Then, in the state of FIG. 12 rotated 90 degrees clockwise from the state of FIG. 11, the point X coincides with the center O of the drive shaft 3 and the center OH of the planetary cam 13, and eventually the stroke S1 is divided. Only the reciprocating body 5 is moved rightward.

  On the other hand, since the planetary cam 13 is fitted in the cam hole 15 of the reciprocating body 5, the vertical movement is restricted, and even if the reciprocating body 5 moves in the left-right direction, the planetary cam 13 The distance from the point D (the uppermost end and the lowermost end) located at the farthest position on the circumference of the circle 13 to the horizontal line H passing through the center O of the drive shaft 3 is always constant (the radius r of the planetary cam). Therefore, in the vertical line V2 passing through the center OP of the planetary cam 13, the radius r is a point where the circumference (including the thickness of the bearing 12) of the eccentric cam 10 and the vertical line V2 intersect from the center OP of the eccentric cam 10. It is the same as the dimension obtained by adding the dimension OP-C to C and the wall thickness dimension CD of the planetary cam 13 from the point C to the point D where the circumference of the planetary cam 13 intersects the vertical line V2.

  Under such conditions, when the eccentric cam 10 rotates 90 degrees clockwise from the state shown in FIG. 11 to the state shown in FIG. 12, the center OH of the eccentric cam 10 changes from the horizontal line H upward. The dimension OP-C from the center OP of the planetary cam 13 to the point C where the circumference of the eccentric cam 10 intersects the vertical line V2 increases by the dimension (OH-H) that the eccentric cam 10 has shifted upward. To do. For this reason, the wall thickness dimension DC of the planetary cam 13 between the point C on the circumference of the eccentric cam 10 and the point D on the circumference of the planetary cam 13 is reduced by an amount corresponding to the increase in OP-C. Must be.

  However, since the planetary cam 13 is fitted in the cam hole 15 of the reciprocating moving body 5 and the movement in the vertical direction is restricted, the planetary cam 13 inevitably has a thickness decreasing direction, that is, an eccentric cam. The counterclockwise rotation is opposite to the clockwise rotation of 10. When the rotation of the planetary cam 13 in the counterclockwise direction is viewed from the center O of the drive shaft 3 in the direction of the horizontal line H, the planetary cam 13 on the horizontal line H changes in the direction of increasing thickness on the right side of the center O. Then, the reciprocating body 5 is pushed and moved in the right direction by the increased dimension. Then, in the state of FIG. 12 in which the eccentric cam 10 is rotated 90 degrees clockwise from the state of FIG. 11, the planetary cam 13 has moved the reciprocating moving body 5 to the right by the dimension of the stroke S2.

  In short, in the state shown in FIG. 12, the center O of the drive shaft 3 and the center OP of the planetary cam 13 coincide, and the center OH of the eccentric cam 10 is above the horizontal line H and above the vertical line V. And is shifted upward from the center O of the drive shaft 3 by the same dimension as the stroke S1. The reciprocating body 5 has moved the reciprocating body 5 from the state shown in FIG. 11 to the right by the dimension S3 obtained by adding the stroke S1 due to the movement of the eccentric cam 10 and the stroke S2 due to the movement of the planetary cam 13. become. At this time, the reciprocating body 5 is located at an exactly middle point of the moving stroke in the left-right direction.

  Next, the case where the rotation of the drive shaft 3 proceeds and the eccentric cam 10 moves from the position of the intermediate point in FIG. 12 to the right dead center shown in FIG. 13 will be described. In the state of FIG. 12, the point A on the circumference of the eccentric cam 10 is at a position on the vertical line V passing through the center O of the drive shaft 3. When the drive shaft 3 is further rotated 90 degrees clockwise from this state, the point A on the circumference of the eccentric cam 10 rotates so as to be positioned on a horizontal line H passing through the center O of the drive shaft 3. Accordingly, the center OH of the eccentric cam 10 moves from the position on the vertical line V to the horizontal line H. On the horizontal line H, it is at a position away from the center O of the drive shaft 3 to the right by the stroke S1. As a result, the rotation of the eccentric cam 10 moves the reciprocating body 5 to the right via the planetary cam 13 by the dimension of the stroke S1.

    On the other hand, when the eccentric cam 10 rotates 90 degrees clockwise from the intermediate point state of FIG. 12 to the right dead center state shown in FIG. 13, the center OH of the eccentric cam 10 is on the vertical line V. It shifts from the position to the position on the horizontal line H. This rotational displacement of the eccentric cam 10 changes the thickness of the planetary cam 13 by the amount of the displacement. That is, the dimension OP-C from the center OP of the planetary cam 13 to the point C where the circumference of the eccentric cam 10 intersects the vertical line V2 is equal to the dimension (OH-H) that the eccentric cam 10 has shifted downward. Decrease. Therefore, the thickness dimension DC of the planetary cam 13 from the point C on the circumference of the eccentric cam 10 to the point D on the circumference of the planetary cam 13 must be increased.

  However, since the planetary cam 13 is fitted in the cam hole 15 of the reciprocating moving body 5 and the movement in the vertical direction is restricted, the planetary cam 13 inevitably has a thickness increasing direction, that is, an eccentric cam. The counterclockwise rotation is opposite to the clockwise rotation of 10. When the rotation of the planetary cam 13 in the counterclockwise direction is viewed from the center O of the drive shaft 3 in the direction of the horizontal line H, the planetary cam 13 on the horizontal line H increases on the right side of the center O in a direction in which the wall thickness increases. Then, the reciprocating body 5 is pushed and moved in the right direction by the increased dimension. In the state of FIG. 13 in which the eccentric cam 10 is rotated 90 degrees clockwise from the state of FIG. 12, the planetary cam 13 has moved the reciprocating body 5 to the right by the stroke S2.

  In the state shown in FIG. 13, the center OH of the eccentric cam 10 is on a horizontal line H that is separated from the center O of the drive shaft 3 by the stroke S1 in the right direction, and the center OP of the planetary cam 13 is the center OH of the eccentric cam 10. Is on a horizontal line H that is separated to the right by the stroke S2. The point A on the circumference of the eccentric cam 10 farthest from the center O of the drive shaft 3 is also on the horizontal line H, and the point B on the circumference of the planetary cam 13 farthest from the center OH of the eccentric cam 10 is also a horizontal line. On H. In the state shown in FIG. 13, the reciprocating body 5 is at the position of the right dead center that has moved to the right most, and has moved from the position of the intermediate point by the stroke S1 + S2.

  Similarly, when the drive shaft 3 is rotated 90 degrees clockwise from the right dead center state shown in FIG. 13, the intermediate point state shown in FIG. 14 is obtained. The center OH of the eccentric cam 10 rotationally moves from a position on the horizontal line H to a position on the vertical line V of the drive shaft 3 so as to be positioned away from the center O of the drive shaft 3 by an eccentric dimension. Become. Looking at the amount of shift of the center OH of the eccentric cam 10 in the horizontal line H direction at this time, it is moved to the left by the dimension of the stroke S1. This movement of the eccentric cam 10 means that the reciprocating body 5 is moved to the left by the stroke S1 through the planetary cam 13.

  On the other hand, in the planetary cam 13, since the point A on the circumference of the eccentric cam 10 rotates clockwise to the position on the vertical line V, the center OH of the eccentric cam 10 from the horizontal line H as described above. It will shift downward. Here, when the eccentric cam 10 is shifted downward, the circumference of the eccentric cam 10 intersects the vertical line V2 from the center OP of the planetary cam 13 by the amount (OH-H) of the shifted dimension. The dimension OP-C up to C increases. Therefore, the thickness dimension DC of the planetary cam 13 from the point C on the circumference of the eccentric cam 10 to the point D on the circumference of the planetary cam 13 must be small.

However, as described above, since the planetary cam 13 is fitted into the cam hole 15 of the reciprocating moving body 5 and the vertical movement is restricted, the planetary cam 13 inevitably has a small thickness. From the state shown in FIG. 13, the motor rotates counterclockwise. The rotation of the planetary cam 13 in the counterclockwise direction changes in a direction in which the wall thickness of the planetary cam 13 on the horizontal line H increases on the left side of the center O when viewed in the direction of the horizontal line H from the center O of the drive shaft 3. Then, the reciprocating body 5 is pushed and moved to the left by the increased dimension. In the state of the intermediate point in FIG. 14, the planetary cam 13 has moved the reciprocating body 5 to the left by the stroke S2.
That is, the eccentric cam 10 moves the reciprocating body 5 to the left by the dimension of the stroke S1 from the state of FIG. 13, and the planetary cam 13 moves the reciprocating body 5 to the left by the dimension of the stroke S2 from the state of FIG. 14 and the state of the intermediate point in FIG. 14 is obtained.

  Next, the case where the rotation of the drive shaft 3 further proceeds and the eccentric cam 10 moves from the position of the intermediate point in FIG. 14 to the left dead center shown in FIG. 11 will be described. When the drive shaft 3 is further rotated 90 degrees clockwise from the state of FIG. 14, the point A on the circumference of the eccentric cam 10 rotates and moves so as to be positioned on a horizontal line H passing through the center O of the drive shaft 3. . Accordingly, the center OH of the eccentric cam 10 moves from the center O of the drive shaft 3 to the horizontal line H that is separated to the left by the stroke S1. As a result, the reciprocating body 5 is moved to the left via the planetary cam 13 by the dimension of the stroke S1.

    On the other hand, in the planetary cam 13, the center OH of the eccentric cam 10 changes from a position on the vertical line V to a position on the horizontal line H. The rotational displacement of the eccentric cam 10 is a point C where the circumference of the eccentric cam 10 intersects the vertical line V2 from the center OP of the planetary cam 13 by the dimension (OH-H) that the eccentric cam 10 has shifted upward. The dimension OP-C up to is increased. Therefore, the thickness dimension DC of the planetary cam 13 between the point C on the circumference of the eccentric cam 10 and the point D on the circumference of the planetary cam 13 must be reduced. Since the planetary cam 13 is restrained from moving up and down, it rotates in the counterclockwise direction. When the rotation of the planetary cam 13 in the counterclockwise direction is viewed from the center O of the drive shaft 3 in the direction of the horizontal line H, the planetary cam 13 on the horizontal line H on the left side of the center O changes in a direction in which the wall thickness increases. Then, the reciprocating body 5 is pushed and moved to the left by the increased dimension. In the state of FIG. 11, the planetary cam 13 has moved the reciprocating body 5 to the left by the stroke S2.

  As described above, in the state of the left dead center in FIG. 11, the center OH of the eccentric cam 10 is on the horizontal line H that is leftward from the center O of the drive shaft 3 by the stroke S1, and the center OP of the planetary cam 13 is It is on a horizontal line H that is leftward from the center OH of the eccentric cam 10 by the stroke S2. The point A on the circumference of the eccentric cam 10 farthest from the center O of the drive shaft 3 is also on the horizontal line H, and the point B on the circumference of the planetary cam 13 farthest from the center OH of the eccentric cam 10 is also a horizontal line. On H. In the state shown in FIG. 11, the reciprocating body 5 is at the position of the left dead center that has moved to the left most, and has moved from the position of the intermediate point by the dimension of the stroke S1 + S2.

    The rotary cam mechanism 4 including the eccentric cam 10 and the planetary cam 13 repeats the above steps to reciprocate the reciprocating body 5 in the left-right direction, thereby functioning as a vacuum pump. By the way, in the position of the intermediate point shown in FIG.12 and FIG.14, the force which the rotary cam mechanism 4 of the eccentric cam 10 and the planetary cam 13 tries to push out this in order to move the reciprocating body 5 to the left-right direction. Is not enough. Therefore, in this embodiment, the push cam 11 of the composite cam body 9 shown in FIGS. 5 and 6 pushes the reciprocating body 5 with a strong torque at the intermediate point position. In other words, the push cam 11 is eccentrically mounted on the drive shaft 3, and the upper and lower circumferential curved surfaces of the sliding guide surface 16 are positioned at the midpoint position of the reciprocating moving body 5 shown in FIGS. 12 and 14. It is set to be surface bonded. Therefore, when the drive shaft 3 is rotated, the rotational driving force of the drive shaft 3 is directly transmitted from the position of the intermediate point to the reciprocating body 5 through the surface joining portion of the extrusion cam 11 and the circumferential curved surface 16. Be pushed out with great force. Thereby, a smooth reciprocating movement is possible. After the reciprocating body 5 starts moving from the position of the intermediate point, the rotational driving force of the drive shaft 3 is transmitted to the reciprocating body 5 by the rotary cam mechanism 4 described above.

  Next, the suction / exhaust operation of the vacuum pump by the reciprocating operation of the reciprocating body 5 will be described. In the state of the left dead center shown in FIG. 11, the piston 6A attached to the left end side of the reciprocating body 5 is in a position where the volume of the pressure chamber 7A is minimum, and the exhaust is finished. Further, the piston 6B attached to the right end side of the reciprocating body 5 is in a position where the volume of the pressure chamber 7B is maximized, and the intake is completed. When the drive shaft 3 rotates 90 degrees clockwise from this left dead center state, the reciprocating moving body 5 moves to the position of the intermediate point shown in FIG. 12, the pistons 6A and 6B move to the pressure chambers 7A and 7B. In the pressure chamber 7A, half intake is performed, and in the pressure chamber 7B, half exhaust is performed.

As for the intake air in the pressure chamber 7A, the pressure chamber 7A becomes negative pressure due to the piston 6A moving in the right direction. Therefore, the valve 32 of the intake valve 26 warps in the right direction in FIGS. The hole 29 is opened. For this reason, intake is performed from the intake port 23 to the pressure chamber 7A through the intake chamber 21, the intake hole 33 of the exhaust valve 28, and the intake hole 29 of the valve body 25.
As for the exhaust in the pressure chamber 7B, the pressure chamber 7B becomes a positive pressure as the piston 6B moves in the right direction. Therefore, the valve 27 of the exhaust valve 28 warps in the right direction in FIGS. The hole 30 is opened. Therefore, the air in the pressure chamber 7 </ b> B is discharged to the exhaust chamber 22 through the exhaust hole 31 of the intake valve 26 and the exhaust hole 30 of the valve body 25 and is exhausted to the outside from the exhaust port 24.

  When the drive shaft 3 further rotates 90 degrees from the state of the intermediate point shown in FIG. 12 and the reciprocating body 5 moves to the position of the right dead center shown in FIG. 13, the volume in the pressure chamber 7A becomes maximum, and in the pressure chamber 7B Volume is minimized. Therefore, the intake is completed in the pressure chamber 7A, and the exhaust is completed in the pressure chamber 7B. Further, in the state of FIG. 14 in which the drive shaft 3 further rotates 90 degrees from the state of the right dead center shown in FIG. 13 and the reciprocating body 5 returns to the position of the intermediate point, the pistons 6A and 6B are connected to the pressure chambers 7A and 6A. 7B returns to an intermediate position. Thereby, half exhaust is performed in the pressure chamber 7A, and half intake is performed in the pressure chamber 7B.

  When the drive shaft 3 further rotates 90 degrees from the intermediate point state shown in FIG. 14 and the reciprocating body 5 moves to the position of the left dead center shown in FIG. 11, the volume in the pressure chamber 7A becomes minimum, and the pressure chamber 7B Then the volume is maximized. For this reason, the exhaust is completed in the pressure chamber 7A, and the intake is completed in the pressure chamber 7B.

  The present invention is not limited to this embodiment, and appropriate modifications are possible. For example, the case where the reciprocating body 5 is a piston support that reciprocates the pistons 6A and 6B of the vacuum pump 1 has been described as an example, but it can also be applied to a plunger pump that sucks and discharges water and other liquids. It is also applicable as a priming pump for fire fighting pumps. Further, it can be applied as a refrigerant compressor of a compressor. Furthermore, as long as the rotary motion is converted into a linear reciprocating motion, it can be applied to other than the pump.

DESCRIPTION OF SYMBOLS 1 ... Vacuum pump 2 ... Casing 3 ... Drive shaft 4 ... Rotary cam mechanism 5 ... Reciprocating moving body 6A, 6B ... Piston 7A, 7B ... Pressure chamber 8A, 8B ... Valve body 9 ... Composite cam body 10 ... Eccentric cam 11 ... Extrusion Cam 12 ... Bearing 13 ... Planetary cam 14 ... Bearing 15 ... Cam hole 16 ... Sliding guide surface 17 ... Pushing force forming part

Claims (6)

  A reciprocating body mounted in a casing so as to be capable of reciprocating; a drive shaft disposed in a direction perpendicular to the reciprocating direction of the reciprocating body; an eccentric cam mounted on the drive shaft; A rotary cam type comprising a planetary cam that is eccentrically fitted on the outer peripheral surface of the eccentric cam and is rotatably fitted and mounted in a cam hole provided in the reciprocating body. Reciprocating body.   A reciprocating body mounted in a casing so as to be capable of reciprocating; a drive shaft disposed in a direction perpendicular to the reciprocating direction of the reciprocating body; an eccentric cam mounted on the drive shaft; A planetary cam that is rotatably eccentrically fitted on the outer peripheral surface of the eccentric cam and is rotatably fitted in a cam hole provided in the reciprocating body, and a back surface side of the reciprocating body. A rotary cam comprising: a pushing force forming portion having an oblong sliding guide surface; and a push cam that is eccentrically mounted on the drive shaft and fitted to the pushing force forming portion. Reciprocating body.   The rotary according to claim 1 or 2, wherein the drive shaft and the planetary cam are in a concentric positional relationship at an intermediate point of the reciprocating stroke, and the eccentric cam is in a positional relationship that is eccentric by a predetermined dimension from the center of the drive shaft. Cam reciprocating body.   A reciprocating body mounted in the casing so as to be reciprocally movable; a piston attached to a tip end side of the reciprocating body; and a drive shaft disposed in a direction perpendicular to the reciprocating direction of the reciprocating body. And an eccentric cam mounted on the drive shaft, and eccentrically mounted on the outer peripheral surface of the eccentric cam so as to be rotatably fitted and fitted to a cam hole provided in the reciprocating body. Corresponding to the planetary cam, the pressure chamber whose volume ratio changes due to the reciprocating movement of the reciprocating body and piston in the casing, the inlet and outlet formed in the pressure chamber, and the reciprocating movement of the reciprocating body and piston A pump comprising a valve body that automatically opens and closes the inflow port and the discharge port.   A reciprocating body mounted in the casing so as to be reciprocally movable; a piston attached to a tip end side of the reciprocating body; and a drive shaft disposed in a direction perpendicular to the reciprocating direction of the reciprocating body. And an eccentric cam mounted on the drive shaft, and eccentrically mounted on the outer peripheral surface of the eccentric cam so as to be rotatably fitted and fitted to a cam hole provided in the reciprocating body. A planetary cam, a pushing force forming portion provided on the back side of the reciprocating moving body and having an oblong sliding guide surface, and attached eccentrically on the drive shaft and fitted to the pushing force forming portion. It corresponds to the reciprocating movement of the reciprocating body and the piston, the pressure chamber whose volume ratio is changed by the reciprocating movement of the reciprocating body and piston in the casing, the inlet and outlet formed in the pressure chamber, and the reciprocating body and piston. The inlet and outlet Pump, characterized in that is constituted by a valve body for opening and closing.   6. The pump according to claim 4, wherein the drive shaft and the planetary cam are in a concentric positional relationship at an intermediate point of the reciprocating stroke, and the eccentric cam is in a positional relationship that is eccentric by a predetermined dimension from the center of the drive shaft. .

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