JP2008525718A - Rotary pump - Google Patents

Abstract

The present invention relates to a rotary pump that performs pumping by using a suction input of a rotor that rotates via a rotary motor, and makes it easy to switch between high speed and low speed by eccentrically rotating the shaft of the rotary motor so that the rotor rotates eccentrically. The present invention relates to a rotary pump having a space inside the body to prevent breakage of a partition plate, and smooth rotation motion is performed by bearing means.
Therefore, the rotary pump according to the present invention applies a steel ball and a needle pin to the rotor to minimize the friction generated between the inner circumferential surface of the volume chamber and the outer circumferential surface of the eccentric rotating body by a rolling motion. Easy rotation.
Further, the present invention has a space between the volume chamber and the outer peripheral surface of the eccentric rotor, and has a high durability in which the problem of breakage due to torsional stress and tensile force of the conventional diaphragm is absorbed by the space. It is an invention.

Description

The present invention relates to a rotary pump that pumps fluid using suction input of a rotor that is rotated by a rotary motor, and makes it easy to switch between high speed and low speed by eccentrically rotating the shaft of the rotary motor so that the rotor rotates eccentrically. The present invention relates to a rotary pump having a space inside the body to prevent breakage of a partition plate, and smooth rotation motion is performed by bearing means.

In general, a pump is a machine that is used to move fluid from low to high or move fluid elsewhere.

  However, the conventional pump has many problems.

  Hereinafter, typical conventional pumps and their problems will be described.

  FIG. 1 shows a rotary pump in which an upper rotor 2 disposed in an upper volume chamber 1 is connected to a lower rotor 4 disposed in a lower volume chamber 3 via a diaphragm 5.

  As shown in the upper left of FIG. 1, when the upper rotor 2 and the lower rotor 4 are located directly above the rotary pump, the rotary pump has an eccentric rotation point of the upper rotor 2 and an eccentric rotation point of the lower rotor 4. The distance between them is minimized.

  That is, the distance between the upper rotor 2 and the lower rotor 4 is minimized.

  Next, as shown in the upper right of FIG. 1, when the upper rotor 2 and the lower rotor 4 are positioned diagonally (inclination direction), the eccentric rotation point of the upper rotor 2 and the eccentric rotation point of the lower rotor 4 The distance between is maximized.

  That is, the distance between the upper rotor 2 and the lower rotor 4 is maximized.

  More specifically, with reference to a specific example, as shown in FIG. 1, when the upper rotor 2 and the lower rotor 4 are located directly above, the eccentric rotation point of the upper rotor 2 and the eccentric rotation of the lower rotor 4 The distance between the points is 175.2 mm.

  At this time, the distance between the upper rotor 2 and the lower rotor 4 is 61.2 mm.

  As shown in FIG. 1, when the upper rotor 2 and the lower rotor 4 are located diagonally, the distance between the eccentric rotation point of the upper rotor 2 and the eccentric rotation point of the lower rotor 4 is 177.2 mm. .

  At this time, the distance between the upper rotor 2 and the lower rotor 4 is 63.2 mm.

  Here, when the partition plate 5 connecting the upper rotor 2 and the lower rotor 4 is a rigid body, the structure and operation of the rotary pump rotor shown in FIGS. 1a and 1b cannot be realized.

  In other words, the length of the partition plate 5 must be changed according to the position of the rotor.

  In order to solve such a problem, as shown in FIG. 2, the “double cylindrical pump” disclosed in Korean Patent Application No. 1994-010299 is a first sliding body 1 (hereinafter referred to as “upper part”). The partition plate 3 is inserted into the sliding groove 2 formed on the outer peripheral surface of the rotor “), and the partition plate 3 is detachably connected to the upper rotor 1, and the second sliding body 4 (hereinafter,“ It is integrally connected to the “lower rotor”.

  Therefore, when the upper rotor 1 and the lower rotor 4 are positioned diagonally (inclined direction), the partition plate 3 slides in the sliding groove 2 of the upper rotor 1, and the distance between the upper rotor 1 and the lower rotor 4. Becomes variable.

  However, in the system in which the partition plate 3 is inserted into the sliding groove 2 of the upper rotor 1 to change the distance between the upper rotor 1 and the lower rotor 4, the upper and lower rotors 1, 4 are rotated during the rotation. Since the plate 3 slides in the sliding groove 2, the partition plate 3 may be detached from the upper rotor. Further, when applied to a multi-stage rotary pump, the rotational force (torque) acts on the upper rotor 1 prior to the sliding of the partition plate 3 in the sliding groove 2, so that the eccentric shaft that rotates the upper rotor 1 is used. However, it receives torsional stress. As a result, the eccentric shaft, the rotors 1 and 4 and the partition plate 3 may be damaged.

  Therefore, in order to solve such a problem, a method of using an eccentric gear to maintain a constant distance between the upper rotor and the lower rotor is also used.

  However, when this method is also applied to a multistage rotary pump, the eccentric gear causes the eccentric shaft to drive the upper rotor clockwise and the lower rotor to rotate counterclockwise, generating torsional stress. To do.

  In the single-stage rotary pump, the eccentric gear can be used. However, in the case of a multi-stage rotary pump, the phase of the rotor attached to the shaft is different, the acceleration section is changed by the eccentricity, and the rotor may be damaged. Increases nature.

  The present invention for solving the above-described problems is a rotary pump that pumps a fluid using suction input of a rotor that rotates via a rotation (drive) motor, and the shaft of the rotation motor is set to one side. Provide a rotary pump that makes it easy to switch between high speed and low speed by making it eccentric, has a space inside the eccentric rotor of the rotor, prevents breakage of the partition plate, and allows smooth rotation movement by bearing means To do.

  Accordingly, the present invention provides a rotary pump having a drive motor and upper and lower volume chambers, and pumping with a rotor and a partition plate that rotate along the inner peripheral surface of the volume chamber. A rotating motor in which an overload prevention device having a helical gear is fixed to the shaft end thereof is fixed, a transmission unit fixed to the end of the overload prevention device, and movement of the transmission unit. A transmission unit includes a volume chamber at both upper and lower ends in which a receiving rotor is housed, and a rotor formed with an eccentric rotating body including a bearing means that performs a circular motion by a pair of rotating shafts eccentrically disposed inside the pair of rotors. The number of rotations of the rotary motor is controlled by, and the rotor performs pumping rotation to pump fluid outside the volume chamber.

  Further, the transmission unit fixed to the overload prevention tool, which is a main part of the present invention, meshes with a helical gear eccentric to one side, and a first gear fitted to the rotation shaft on the other side in the eccentric direction, A first auxiliary gear having a smaller diameter than the first gear integrally fixed to the lower stage of the first gear; a second gear having a long diameter which meshes with the first auxiliary gear and serves as a rotation shaft on the other side; A second auxiliary gear having a smaller diameter than the second gear integrally fixed to the lower stage of the second gear, and a third gear having a large diameter which meshes with the second auxiliary gear and is externally fitted to the other rotating shaft. And a third auxiliary gear having a smaller diameter than the third gear integrally fixed to the lower stage of the third gear, and a large diameter first gear which meshes with the third auxiliary gear and is externally fitted to the other rotation shaft. 4 gears and a 4th gear having a smaller diameter than the 4th gear fixed integrally to the lower stage of the 4th gear. A fifth gear having a long diameter that meshes with the gear and the fourth auxiliary gear and is externally fitted to the rotation shaft on the other side, and a fifth gear that is smaller in diameter than the fifth gear that is integrally fixed to the lower stage of the fifth gear. 5 auxiliary gears, a large-diameter driving gear meshed with the fifth auxiliary gear and keyed to the other rotary shaft, and first and second key fixed to the pair of rotary shafts with the same diameter When the main gear is connected to the first gear and the first auxiliary gear or the fifth gear and the fifth auxiliary gear with the rotating shaft, a bearing is built in to induce low-speed idling and rotation of the driving gear. By transmitting force, the first and second main driving gears rotate at a low speed, and the rotor rotates at a low speed.

  Note that another embodiment of the transmission unit fixed to the load preventing device, which is the main part of the present invention, meshes with a helical gear eccentric to one side and is externally fitted to the rotation shaft on the other side in the eccentric direction. One gear, a first auxiliary gear having a larger diameter than the first gear integrally fixed to the lower stage of the first gear, and a short diameter that meshes with the first auxiliary gear and is externally fitted to the rotation shaft on the other side. The second gear, the second auxiliary gear having a diameter larger than that of the second gear integrally fixed to the lower stage of the second gear, and the second auxiliary gear mesh with each other and are fitted on the rotary shaft on the other side. A third gear having a short diameter, a third auxiliary gear having a diameter larger than that of the third gear integrally fixed to the lower stage of the third gear, and the third auxiliary gear mesh with each other, and are fitted on the rotary shaft on the other side. The smaller diameter fourth gear and the fourth gear fixed integrally to the lower stage of the fourth gear are smaller in diameter. A small fourth driving gear meshing with the fourth auxiliary gear and keyed to the other rotating shaft; and first and second keys fixed to the pair of rotating shafts with the same diameter. When the first gear and the first auxiliary gear or the fourth gear and the fourth auxiliary gear are coupled to the rotating shaft, a bearing is built in to induce high-speed idling, Provided is a rotary pump in which first and second main driving gears are rotated by transmission of rotational force to rotate a rotor at high speed.

  Further, the rotor which is another main part of the present invention is a cylindrical shape having a diameter smaller than the inner peripheral surface of the volume chamber, and a cylindrical housing having a circular space on the inner peripheral surface, and the cylindrical type An eccentric rotating body having a diameter smaller than that of the inner peripheral surface of the housing and having a rotating shaft fastened in an eccentric state on one side and having a number of concave grooves around the outer peripheral surface, and the eccentric rotation Bearing means seated in a number of concave grooves of the body, the cylindrical housing and the eccentric rotating body are respectively accommodated in the volume chambers at the upper and lower ends, and both are connected via a partition plate in the eccentric direction. Provide a rotating rotary pump.

  In addition, another embodiment of the rotor, which is the main part of the present invention, has a cylindrical shape having a small diameter compared to the inner peripheral surface of the volume chamber, and a cylindrical housing having a circular space on the inner peripheral surface thereof. An eccentric rotating body having a diameter smaller than the inner peripheral surface of the cylindrical housing, the rotating shaft being fastened in an eccentric state on one side, and a plurality of concave grooves formed around the outer peripheral surface; And the bearing means inserted into a number of concave grooves of the eccentric rotator, the cylindrical casing and the eccentric rotator are respectively accommodated in the volume chambers at the upper and lower ends, and both are connected via a partition, A rotary pump that rotates in a specified direction is provided.

As described above, the rotary pump according to the present invention applies a steel ball and a needle pin to the rotor to bring the inner peripheral surface of each volume chamber and the eccentric rotating body into rolling contact with each other, thereby reducing the friction between them. Therefore, smooth rotation of the rotor is guaranteed.

  Further, the present invention secures a space between the volume chamber and the outer peripheral surface of the eccentric rotor, solves the conventional problem of breakage due to torsional stress and tensile force of the diaphragm, and improves the durability of the pump. Improvements can be made.

  Furthermore, since the present invention includes an overload prevention tool, even if an overload acts on the rotor portion and the transmission unit, the transmission unit can be prevented from being damaged, and the durability of the invention is further improved.

  First, the present invention is the Korean priority application of Korean Patent Application Nos. 2004-0114504 and 2005-0090212.

  The present invention is similar to the conventional one in that it is a rotary pump that has a drive motor, upper and lower volume chambers, a rotor that rotates along the inner peripheral surface of the volume chamber, and a diaphragm. is doing.

  However, in the present invention, an eccentric rotating body is provided inside the rotor, and a space portion is formed between the rotor and the eccentric rotating body, and the length of the partition plate is variable depending on the space portion, unlike the conventional one. It becomes unnecessary to do. Furthermore, another feature of the present invention is that the rotational speed can be switched between high speed and low speed by the transmission unit. Hereinafter, it will be described in detail with reference to the accompanying drawings.

  First, in order to explain the present invention more clearly, the operation of the rotor will be described with reference to FIG.

  The rotary pump of the present invention includes a pair of rotors 200 that rotate inside two circular volume chambers 30 at the upper and lower portions, like a general rotary pump.

  That is, as shown in FIG. 3, the upper rotor 200 (upper part with reference to the drawing shown) rotates clockwise, and the lower rotor 200 (lower part with reference to the drawing shown) rotates counterclockwise. Rotate around.

  Accordingly, as shown sequentially, first, the upper rotor 200 is erected vertically with the uppermost portion of the upper volume chamber 30 in contact with the upper volume chamber 30, and then the upper rotor 200 rotates 90 degrees clockwise. The contact surface of the upper rotor 200 is displaced to a portion of the upper volume chamber 30 (upper portion with reference to the drawing shown) that is 90 ° away from the uppermost portion.

  At this time, the lower rotor 200 (lower part with reference to the drawing shown) is rotated 90 degrees counterclockwise, and the contact surface of the lower rotor 200 is 270 ° away from the uppermost part (shown in the lower volume chamber 30 (shown). Displace to the lower part of the drawing.

Next, the upper rotor 200 rotates clockwise until it reaches a portion of the upper volume chamber 30 that is 180 degrees away from the top. At this time, the lower rotor 200 is
It rotates counterclockwise until it reaches the portion of the lower volume chamber 30 that is 180 degrees away from the top.

Next, the upper rotor 200 rotates clockwise until it reaches the inner surface portion of the upper volume chamber 30 that is 270 degrees away from the top. At the same time, the lower rotor 200
It rotates counterclockwise until it reaches the portion of the lower volume chamber 30 that is 270 degrees away from the top.

  Thereafter, return to the beginning and repeat the rotation.

  Here, unlike the case where the upper rotor 200 rotates clockwise and the lower rotor 200 rotates counterclockwise, the upper rotor 200 rotates counterclockwise and the lower rotor 200 rotates clockwise. It doesn't matter.

  By such rotation, the fluid is sucked from the inlet BC of the volume chamber 30 and discharged to the outlet BD.

  Hereinafter, the reason why the partition plate 207 connecting the upper rotor 200 and the lower rotor 200 described in the prior art becomes longer or shorter due to this rotation will be described with reference to FIG.

  In FIG. 4, the diameter of the rotor 200 is greatly reduced for ease of explanation.

  As shown in FIG. 4, in a state where the upper rotor 200 and the lower rotor 200 are set up vertically, the length of the partition plate is AB, which is equal to the length AC (AB = AC).

  That is, when the upper rotor 200 rotates clockwise and reaches the inner surface portion of the upper volume chamber 30 that is 90 degrees away from the uppermost part, the lower rotor 200 also rotates counterclockwise and is separated from the uppermost part by 90 degrees. The inner surface of the lower volume chamber 30 is reached.

  At this time, the length of the diaphragm is AK.

  However, the Pythagorean theorem proves that the length of the right triangle is the longest hypotenuse, so further explanation is omitted, but in the present invention, the length of any method is long. Must be.

  Therefore, the conventional technique has a structure in which the length of the partition plate 207 is variable while the diameter of the rotating rotor 200 is constant.

  Such a method has taken up its problems in the prior art, so further explanation is omitted, but in the present invention, an eccentric rotating body 220 is provided inside the rotor 200 to constitute the space portion. Now that we have solved the problem perfectly, we will explain it below.

  The present invention is a state in which the output shaft 11 is eccentric to one side, and there is a rotary motor 10 to which an overload preventer 20 having a helical gear 12 is fixed at the end of the shaft. A transmission (clutch) unit 100 is provided at the end.

  In addition, an upper and lower volume chambers 30 are provided, and a rotor 200 that receives a driving force from the transmission unit 100 is provided in these volume chambers 30. In each rotor 200, there is provided an eccentric rotating body 220 having bearing means 210 that is rotated by rotating shafts S1 and S2.

  Therefore, while the output of the rotation (drive) motor 10 is transmitted to the rotation shaft, the rotation speed of the rotation motor 10 is varied by the transmission unit 100, the rotor 200 performs the popping rotation, and the fluid is transferred to the outside of the volume chamber 30. Pump.

  Specifically, the rotary motor 10 is connected to the pump in a state where the output shaft 11 is biased to one side, that is, is eccentric.

  A helical gear 12 is provided at the end of the shaft to increase its rotational friction.

  And although the transmission unit 100 is fixed to the helical gear 12 which is the shaft end, in this invention, the high-speed transmission unit mentioned later may be applied and the low-speed transmission unit 100 may be applied. .

  On the other hand, the rotational force of the rotary motor 10 of the present invention is transmitted to the rotating shafts S1 and S2 after the rotational speed is changed between the high speed and the low speed by the transmission unit 100, and the eccentric rotating body 220 is rotated by the rotational force. The bearing means 210 allows smooth rotation and pumps the fluid.

  Hereinafter, various embodiments of the transmission unit 100 used in the present invention will be described.

There are four embodiments of the transmission unit 100 used in the present invention.
First, as shown in FIG. 5, the first embodiment is a transmission unit 100 fixed to the overload prevention device 20.

  That is, the low-speed driving gear 110 that meshes with the eccentric helical gear 12 is externally fitted to the rotating shaft S2 that is located on the opposite side of the eccentric direction of the helical gear 12, and is key-fixed to the rotating shaft S2. Is provided on the lower side of the low-speed driving gear 110 in a state in which it is fitted around the rotary shaft S2 and fixed with a key.

  A second main driving gear 112 that meshes with the first main driving gear 111 is externally fitted to the other rotation shaft S1 and is key-fixed to the rotation shaft S1.

  Accordingly, the first main driving gear 111 rotates due to the low speed rotation of the low speed driving gear 110, and the second main driving gear 112 meshing with the first main driving gear 111 rotates in the opposite direction.

  That is, as shown in the figure, the rotary motor 10 of the present invention is inserted at the position where the output shaft 11 is offset to the eccentric position of the pump, specifically, the upper rotor 200 (right side with reference to the drawing). It is arranged so that.

  Of course, the output shaft 11 may be arranged eccentrically so as to be offset toward the lower rotor 200 (left side with reference to the drawing shown).

  In the present invention, the reason why the output shaft 11 is arranged so as to be offset toward the upper rotor 200 side is to easily shift the rotational speed between high speed and low speed, and the output shaft 11 is offset toward the upper rotor 200 side. Accordingly, the space secured between the output shaft 11 and the lower rotor 200 (left side with reference to the drawing shown) is larger than the space secured between the output shaft 11 and the upper rotor 200.

  Therefore, as shown in FIG. 5, a gear having a large diameter can be arranged in a larger space.

  That is, when the small gear rotates the large gear, the rotational speed of the shaft decreases, but in the first embodiment shown in FIG. 5 of the present invention, the low speed driving gear 110 rotates at a low speed.

  After all, when the rotary motor 10 of the present invention rotates, the low speed driving gear 110 having a large diameter meshing with the helical gear 12 rotates at a low speed.

  Of course, at this time, since the low-speed driving gear 110 is key-fixed to the rotation shaft S2, the rotation shaft S2 and the low-speed driving gear 110 rotate at the same angular velocity.

  The first main driving gear 111 is key-fixed to the lower rotation shaft S2 of the low speed driving gear 110.

  Therefore, the rotation speed of the first main driving gear 111 is also the same as the rotation speed of the rotation shaft S2.

  Further, the second main driving gear 112 that meshes with the first main driving gear 111 is key-fixed to the other rotating shaft S1, and these rotating shafts S1 and S2 are respectively rotated by the eccentric rotating body 220 to the eccentric rotating body 220. The body 220 is connected so as to be eccentric.

  Eventually, the rotation shafts S1 and S2 rotate in opposite directions to rotate the rotor 200, and this action pumps the fluid at a low speed.

  Of course, the present invention can be used not only for fluids, but also for pneumatic pressures of gases, allowing for air pinning.

  On the other hand, the second embodiment of the transmission unit 100 described above has a high-speed configuration as shown in FIG.

  That is, the high-speed driving gear 120 is provided on the narrow side that is offset to the right side in the drawing in the space secured between the rotating shaft and the output shaft of the motor 10.

  Since this gear has a small diameter, it can rotate at high speed.

  The configuration will be described with reference to FIG. 6. The transmission unit 100 fixed to the overload prevention device 20 includes a high-speed driving gear 120 that meshes with the helical gear 12 that is eccentrically arranged on one side, in the eccentric direction of the helical gear 12. The first main driving gear 121 is externally fitted to the rotary shaft S1 and key-fixed below the high-speed driving gear 120.

  A second main driving gear 122 that meshes with the first main driving gear 121 is externally fitted to the other rotation shaft S2 and key-fixed.

  Therefore, the first main driving gear 121 rotates due to the high speed rotation of the high speed driving gear 120, and the second main driving gear 122 meshing with the first main driving gear 121 rotates in the reverse direction.

  Hereinafter, the operation of the transmission unit 100 will be described with reference to FIG. First, when the rotary motor 10 rotates, the high-speed driving gear 120 that meshes with the helical gear 12 connected to the output shaft of the rotary motor 10 rotates at a high speed.

  Of course, the rotational speed of the high-speed driving gear 120 is slower than the rotational speed of the output shaft of the rotary motor 10.

  As shown, when the high-speed driving gear 120 is rotated by the rotation of the rotary motor 10, the high-speed driving gear 120 is key-fixed to the upper rotary shaft S1 (on the right side with reference to the drawing). Therefore, the upper rotation shaft S1 rotates and the first main driving gear 121 rotates at the same speed.

  Of course, the first main driving gear 121 is also key-fixed to the rotation shaft S1, and the first main driving gear 121 is in a state in which the second main driving gear 122 is engaged as shown in FIG. Therefore, the first main driving gear 121 and the second main driving gear 122 rotate at the same angular velocity in opposite directions.

  Further, since the second main driving gear 122 is key-fixed to the rotation shaft S2, the rotation shaft S2 also rotates at the same angular velocity.

  Eventually, the rotation of the rotary shaft S2 causes a pumping action in order to rotate the rotor part 200 coupled to the end thereof in one or more stages.

  Hereinafter, a third embodiment of the transmission unit 100 of the present invention will be described with reference to FIG.

  That is, the transmission unit 100 of the third embodiment fixed to the overload prevention device 20 meshes with the helical gear 12 eccentric to one side, and is fitted to the rotation shaft S2 on the other side in the eccentric direction. 131 and a first auxiliary gear 132 having a smaller diameter than the first gear 131 integrally fixed to the lower side of the first gear 131, meshes with the first auxiliary gear 132, and is attached to the other rotation shaft S 1. There is a second gear 133 having a long diameter to be fitted and a second auxiliary gear 134 having a smaller diameter than the second gear 133 integrally fixed to the lower side of the second gear 133.

  Compared with the third gear 135 having a long diameter that meshes with the second auxiliary gear 134 and is externally fitted to the other rotation shaft S2, and the third gear 135 that is integrally fixed to the lower side of the third gear 135. There is a third auxiliary gear 136 having a small diameter, which meshes with the third auxiliary gear 136 and is integrally fixed to the lower side of the fourth gear 137 and a fourth gear 137 having a large diameter that is externally fitted to another rotating shaft S1. There is a fourth auxiliary gear 138 having a smaller diameter than that of the fourth gear 137.

  Also, the diameter of the fifth gear 139 is larger than that of the fifth gear 139 that meshes with the fourth auxiliary gear 138 and is externally fitted to the other rotation shaft S2, and the fifth gear 139 that is integrally fixed to the lower stage of the fifth gear 139. There is a small fifth auxiliary gear 140, and there is a large diameter driving gear 144 that meshes with the fifth auxiliary gear 140 and is keyed to the other rotating shaft S <b> 1.

  Further, there are first and second main driving gears 145 and 146 that are key-fixed to the pair of rotating shafts S1 and S2 with the same diameter.

  Accordingly, when the first gear 131 and the first auxiliary gear 132 or the fifth gear 139 and the fifth auxiliary gear 140 are externally fitted to the rotary shafts S1 and S2, the bearing B is interposed so that low-speed idling occurs. The first and second main driving gears 145 and 146 are rotated at a low speed by the transmission of the rotational force of the driving gear 144 and the rotor 200 is rotated at a low speed.

  The transmission unit 100 according to the third embodiment of the present invention will be described below with reference to FIG.

  As shown in FIG. 7, first, when the eccentric helical gear 12 rotates, the first gear 131 having a relatively large diameter rotates.

  At this time, the rotational speed of the rotary motor 10 is reduced.

  However, a first auxiliary gear 132 is integrally provided below the first gear 131, and the first auxiliary gear 132 is very small compared to the diameter of the first gear 131.

  Of course, since the first gear 131 and the first auxiliary gear 132 are integrated, the rotation speed is the same.

  However, the first auxiliary gear 131 meshes with the second gear 133 that is externally fitted to the upper rotation shaft S1 (on the right side with reference to the drawing) on the right side of the drawing. .

  However, the first auxiliary gear 132 has a relatively small diameter, and the second gear 133 has a larger diameter than the first auxiliary gear 132.

  Therefore, when the rotational force is transmitted from the first auxiliary gear 132 to the second gear 133, the rotational speed is decreased.

  On the other hand, as shown in the figure, a second auxiliary gear 132 having a small diameter is also integrally provided below the second gear 133.

  Since these gears are integral, their rotational speed is the same.

  Further, the second auxiliary gear 132 is in a state of meshing with a third gear 135 that is externally fitted to the other rotation shaft S2.

  However, since the third gear 135 has a larger diameter than the second auxiliary gear 134, the rotational speed is reduced when the rotational force is transmitted.

  A third auxiliary gear 136 having a diameter smaller than that of the third gear 135 is integrally provided below the third gear 135.

  After all, since the third gear 135 and the third auxiliary gear 136 are integrated, the rotation speed is kept the same.

  Such a gear connection structure is also applied to the fourth gear 137 and the fourth auxiliary gear 138, and the fifth gear 139 and the fifth auxiliary gear 140, and continuous deceleration is performed.

  Of course, as shown in FIG. 7, the fifth auxiliary gear 140 is in a state in which a relatively large diameter driving gear 144 is engaged with the fifth auxiliary gear 140, and this driving gear 144 is key-fixed to the upper rotation shaft S1. Has been.

  Accordingly, the right rotation shaft S1 is rotated by the rotation of the driving gear 144.

  Since the first gear 131 and the first auxiliary gear 132 to the fifth gear 139 and the fifth auxiliary gear 140 described above are provided with bearings B surrounding the rotation shaft, these gears are connected to the rotation shaft. It rotates smoothly and exhibits a deceleration function.

  Accordingly, the rotation shaft S1 is rotated by the rotation of the driving gear 144, and the first main driving gear 145 on the right side of the driving gear 144 (based on the drawing shown) is rotated by the rotation.

  Of course, the number of rotations of the first main driving gear 145 is the same as that of the driving gear 144 and the rotation shaft S1, and the second main driving gear 146 is engaged.

  Accordingly, the rotation of the first main driving gear 145 calls the rotation of the second main driving gear 146, and the rotations rotate in opposite directions.

  Further, since the second main driving gear 146 is key-fixed to the lower rotary shaft S1, the lower rotary shaft S2 also rotates at the same rotational speed.

  The rotation rotates the rotor 200 connected to the rotation shafts S1 and S2 at both ends, so that the rotor 200 performs an action of pumping fluid.

  In order to further reduce the speed of the transmission unit 100 according to the present invention, sixth to eleventh gears and auxiliary gears are inserted below the fifth gear 139 and the fifth auxiliary gear 140 to reduce the speed. Can be dropped.

  That is, if the gear is continuously connected to the transmission unit 100 in the same manner, the deceleration is continuously performed.

  In order to reduce the deceleration ratio based on this principle, the transmission unit 100 with less deceleration can be obtained by reducing the number of gears in the embodiment described above.

  Of course, the transmission unit 100 of this type is the same as the technical idea of the present invention.

  Hereinafter, a fourth embodiment of the transmission unit 100 of the present invention will be described with reference to FIG.

  Explaining its configuration, the transmission unit 100 fixed to the overload prevention device 20 meshes with the helical gear 12 eccentric to one side, and is externally fitted to the other rotation shaft S2 in the eccentric direction. And a first auxiliary gear 151 having a diameter larger than that of the first gear 150 that is integrally fixed to the lower side of the first gear 150, meshes with the first auxiliary gear 151, and is fitted on the other rotation shaft S <b> 1. The second gear 152 having a relatively small diameter and the second auxiliary gear 153 having a larger diameter than the second gear 152 integrally fixed to the lower side of the second gear 152 are provided.

  Further, a third gear 154 having a relatively small diameter that meshes with the second auxiliary gear 153 and is externally fitted to the other rotation shaft S2, and a third gear 154 that is integrally fixed to the lower side of the third gear 154. There is a third auxiliary gear 155 having a larger diameter than the fourth auxiliary gear 155, which meshes with the third auxiliary gear 155 and is fitted on the other rotating shaft S <b> 1. There is a fourth auxiliary gear 157 having a larger diameter than the fourth gear 156 fixed integrally therewith.

  In addition, there is a relatively small driving gear 158 that meshes with the fourth auxiliary gear 157 and is keyed to the other rotary shaft S2, and is key-fixed to the pair of rotary shafts S1 and S2 with the same diameter. There are 1 and 2 main driving gears 160 and 161.

Therefore, when the first gear 150 and the first auxiliary gear 151 to the fourth gear 156 and the fourth auxiliary gear 157 are externally fitted to the rotation shafts S1 and S2, the bearing B is interposed to induce high-speed idling. The first and second main driving gears 160 and 161 are rotated by transmission of the rotational force of the driving gear 158 to rotate the rotor 200 at a high speed.
Hereinafter, the operation of the transmission unit 100 will be described with reference to FIG. 8. First, when the helical gear 12 fixed to the shaft rotates, the first gear 150 that meshes with the helical gear 12 rotates.

  Of course, the first gear 150 is externally fitted to the lower rotating shaft S2 (left side with reference to the drawing shown), and the first gear 150 has a larger diameter than the first gear 150. The first auxiliary gear 151 is integrally provided.

  Accordingly, the rotation of the first gear 150 calls the rotation of the first auxiliary gear 151, and the number of rotations is the same.

  Then, the rotation of the first auxiliary gear 151 refers to the rotation of the second gear 152 inserted in the upper rotation shaft S1 (the right side with reference to the drawing shown) which is the other side.

  When a gear with a relatively small diameter is rotated by a gear with a large diameter, the number of rotations increases and the gear changes at high speed.

  Accordingly, the rotational speed increases when power is transmitted from the first auxiliary gear 151 to the second gear 152.

  In addition, since the second auxiliary gear 153 having a relatively large diameter is integrated with the second gear 152, the rotational speed of the second auxiliary gear 153 is the same as the rotational speed of the second gear 152. is there.

  When the second auxiliary gear 153 rotates, the third gear 154 that meshes with the gear rotates.

  Also at this time, since the gear with the large diameter rotates the gear with the small diameter, the gear is shifted at a high speed.

  Of course, the third gear 154 is externally fitted to the lower rotary shaft 52 which is the other side, and the third gear 154 has a third auxiliary gear 155 having a large diameter which is integrally formed. So do the same number of rotations.

  On the other hand, the third auxiliary gear 155 is engaged with a fourth gear 156 that is externally fitted to the upper rotation shaft S1 that is the other side.

  Also at this time, since the third auxiliary gear 155 has a large diameter and the fourth gear 156 has a small diameter, the third auxiliary gear 155 is shifted at high speed and transmits rotation.

  In addition, since the fourth gear 156 is connected to a fourth auxiliary gear 157 having a large diameter which is integrally formed, the fourth gear 156 and the fourth auxiliary gear 157 perform the same number of rotations.

  The fourth auxiliary gear 157 is engaged with a small-diameter driving gear 158 that is key-fixed to the lower rotating shaft S2 that is the other shaft.

  Accordingly, the rotation is transmitted from the fourth auxiliary gear 157 having a large diameter to the driving gear 158 having a small diameter, and the speed is changed at a high speed. The driving gear 158 is key-fixed to the lower rotating shaft S2, so that the lower stage The rotation axis S2 (based on the drawing shown) rotates together with the driving gear 158.

  Further, as shown in FIG. 8, the first main driving gear 160 is key-fixed to the right side of the driving gear 158 on the rotating shaft S2, so that the same number of rotations are performed.

  The first main driving gear 160 is in a state where the second main driving gear 161 is engaged with each other, but the diameter is the same.

  Therefore, the rotation of the first main driving gear 160 rotates the second main driving gear 161, but the rotation directions are opposite to each other, and the second main driving gear 161 is also key-fixed to the upper rotation shaft S1. Since it is in a state, the upper rotation shaft S1 also rotates.

  Eventually, the rotational speed of the rotary shaft S2 is changed at high speed by the transmission unit 100 of the fourth embodiment of the invention. Then, the rotation shaft S2 rotates the rotor 200 at the end of the rotation shafts S1 and S2 at a high speed.

  As described above, since the first gear 150 to the fourth gear 156 and the first auxiliary gear 151 to the fourth auxiliary gear 157 are rotatably connected to the rotating shaft via the bearing B, only the speed change function is provided. Demonstrate.

  On the other hand, as shown in FIG. 8, fifth to tenth gears and auxiliary gears are added below the fourth gear 156 and the fourth auxiliary gear 157 (based on the drawing shown). Can be increased at high speed.

  The transmission unit 100 according to the present invention has been described above. Hereinafter, the rotor 200 that is rotated by the rotation of the rotation shafts S1 and S2 that are changed by the transmission unit 100 and exhibits a fluid pumping function will be described in detail. .

  Although the rotor 200 of the present invention can be manufactured in the form of two embodiments, the rotor 200 shown in FIGS. 9 to 12 is the rotor 200 of the first embodiment and is shown in FIGS. The rotor 200 is the rotor 200 of the second embodiment.

  Therefore, first, the rotor 200 of the first embodiment will be described in the order.

  As shown in FIGS. 9 and 10, the rotor 200 of the present invention has a cylindrical shape with a smaller diameter than the inner peripheral surface of the volume chamber 30, and a large number of concave grooves 231 are formed on the inner peripheral surface. In addition, there is a cylindrical casing 230 having a space 235, which includes an eccentric rotating body 220 that is smaller in diameter than the inner peripheral surface of the cylindrical casing 230 and that is externally fitted to the rotary shafts S1 and S2.

  Further, bearing means 210 is seated in the numerous concave grooves 231 of the cylindrical casing 230.

  The cylindrical housing 230 and the eccentric rotator 220 are accommodated in the volume chambers 30 at the upper and lower ends, respectively, and the two cylindrical housings 230 are connected to each other via the partition plate 207 and rotate eccentrically.

  In other words, in the present invention, the rotor 200 refers to a configuration in which a pair of the cylindrical casing 230, the eccentric rotating body 220 and the bearing means 210 existing therein are provided.

  The rotor 200 is positioned inside the volume chamber 30 in which the inlet BC and the outlet BD are formed. The volume chamber 30 is a circular shape, and a large number of concave grooves 231 are provided on the inner peripheral surface thereof. Yes.

  Of course, a needle pin or a ball is seated inside the concave groove 231 so that the rotor 200 can smoothly rotate eccentrically while rotating.

Hereinafter, the operation will be described in more detail.
That is, as shown in FIGS. 9 to 12, the eccentric rotator 220 of the rotor unit 200 is externally fitted to the rotation shafts S1 and S2 connected to the transmission unit 100 of the present invention.

  At this time, the eccentric rotating body 220 is externally fitted to each of the rotation shafts S1 and S2 in an eccentric state, not concentric.

  Accordingly, when the rotation shafts S1 and S2 rotate, the eccentric rotator 220 rotates eccentrically.

  At this time, the eccentric rotator 220 moves along the inner peripheral surface of the volume chamber 30 to suck and discharge the fluid.

  Here, as shown, when the upper eccentric rotator 220 (located in the upper position) rotates clockwise, the lower eccentric rotator 220 (located in the lower position) naturally rotates counterclockwise. .

  On the other hand, the rotary shafts S1 and S2 are arranged concentrically in the volume chambers 30, and the eccentric rotating body 220 is fitted on the rotary shafts S1 and S2 while being eccentric. Therefore, the movement locus of the part farthest from the rotation axis of the eccentric rotator 220 has a shape along the inner peripheral surface of the volume chamber 30.

  At this time, in order to perform the movement more smoothly, a needle pin or a ball is seated in the concave groove 231 provided on the inner peripheral surface of the cylindrical casing 230.

  Accordingly, the outer peripheral surface of the eccentric rotating body 220 abuts on the needle pins and balls of the cylindrical casing 230 and rotates by a rolling action.

  At this time, since each of the eccentric rotating bodies 220 is configured for each of the upper and lower rotors 200, as shown in FIGS. 9 and 10, when the upper rotating shaft S1 rotates clockwise. The eccentric rotating body 220 provided on the rotation shaft S1 also rotates clockwise.

  This rotational motion will be described in more detail. When the rotary shaft S1 rotates in a state where the upper rotor 200 of FIG. 9 is in contact with the uppermost portion of the inner peripheral surface of the upper volume chamber 30 and is located on the vertical line, the rotary shaft S1 is rotated. As a result of this rotation, the eccentric rotator 220 also rotates clockwise, but smooth rotation is performed by the bearing means (ball or needle pin).

  This movement will be described in more detail. As shown in FIG. 9, the upper eccentric rotating body 220 rotates clockwise in a state where it is aligned with the upper portion, and the upper volume chamber in the three o'clock direction of 90 degrees is formed. 30. At this point, the lower eccentric rotating body 220 also rotates counterclockwise and contacts the inner peripheral surface of the lower volume chamber 30 at 270 degrees 9 o'clock. become.

  Next, from the state of the drawing on the right side of FIG. 9, the upper eccentric rotating body 220 further rotates clockwise and comes into contact with the upper volume chamber 30 in the 6 o'clock direction of 180 degrees. Thus, the lower eccentric rotating body 220 further rotates counterclockwise and comes into contact with the inner circumferential surface of the lower volume chamber 30 at 180 ° at 6 o'clock (the drawing on the left side of FIG. 10).

  Further, from the state of the drawing on the left side of FIG. 10, the upper eccentric rotating body 220 further rotates clockwise and comes into contact with the inner peripheral surface of the upper volume chamber 30 in the 270-degree 9 o'clock direction. At that time, the lower eccentric rotating body 220 further rotates counterclockwise and comes into contact with the inner circumferential surface of the lower volume chamber 30 in the 3 o'clock direction of 90 degrees.

  Thereafter, returning to the beginning, the above operation is repeated, and the rotor 200 of the present invention pumps the fluid while rotating.

  Here, the most important aspect of the present invention is that when the rotor 200 is at the position shown in the left drawing of FIG. 9, as described with reference to FIG. 4, the eccentric rotator 220 and the cylindrical housing 230 are arranged. The distance between the contacts is the shortest.

  That is, it means that the distance between the contact points between the eccentric rotor 220 and the cylindrical housing 230 which are the upper and lower rotors 200 is the shortest.

  Of course, the rotation shafts S1 and S2 on which the eccentric rotating body 220 is fitted cannot be shortened or lengthened, and are in a fixed state.

  However, when the rotation shafts S1 and S2 are rotated and are at the positions shown in the drawing on the right side of FIG. 9, as described with reference to FIG. 4, between the eccentric rotator 220 and the cylindrical housing 230, The distance between the contacts is the longest.

  That is, it means that the distance between the contact points between the eccentric rotor 220 as the upper and lower rotor 20 and the cylindrical housing 230 is the longest.

  However, the positions of the rotation axes S1 and S2 cannot be changed.

  Here, how to absorb this difference in distance is important, but in the present invention, the diameter of the eccentric rotating body 220 is designed to be smaller than the diameter of the inner peripheral surface of the cylindrical casing 230.

  Accordingly, a space 235 is secured between them, and the eccentric rotating body 220 can move in the space 235.

  Eventually, such a difference in distance can be compensated for by the cylindrical casing 230 being moved in the space 235 so that the cylindrical casing 230 can be rotated.

  The present invention is further developed from such a concept, and in order to facilitate the organic operation of the eccentric rotating body 220 and the cylindrical casing 230, a concave groove 231 is provided in the cylindrical casing 230. And its depth is different.

  That is, the depth of the concave groove 231 is deeply formed in the order of Gya> G1a> G2a> G3a> Gxa, and is formed in four-way symmetry.

  As shown in FIG. 12, Gya, that is, the depth of the groove formed at the uppermost end of the inner peripheral surface of the cylindrical housing 230 is the deepest, and the next is constant clockwise with respect to Gya. G1a is formed at a position rotated by an angle, and the depth decreases in the order of G2a> G3a> Gxa.

  Eventually, when a ball or needle pin is inserted into the groove 231, as shown in FIG. 11, the protrusion of the ball or needle pin inserted into Gya is the smallest, and the ball or needle pin inserted into Gxa The protrusion is the largest.

  Accordingly, as shown in FIG. 13, the locus of contact of the eccentric rotating body 220 with the ball or needle pin protruding from the inner peripheral surface of the cylindrical housing 230 has a long oval shape at the top and a flat shape at the bottom. It is a circle with a wider degree.

  The action that occurs when such an effect is applied to the present invention is easy to understand when comparing FIG. 13, but while absorbing the distance difference induced in the partition plate 207 of the rotor 200 by the space 235 of the rotor 200, When it is in the position of the groove of Gxa, that is, when the eccentric rotating body 220 of the rotor 200 is positioned from the 3 o'clock direction to the 9 o'clock direction, balls and needle pins are further projected into the cylindrical housing 230.

  The reason for this is that, as shown in the second drawing of FIG. 13, when the eccentric rotating body 220 is positioned in the 6 o'clock direction, all the balls and needle pins seated in the concave groove Gxa are projected. As a result, the outer peripheral surface of the cylindrical casing 230 abuts against the passage and brings about an effect of sealing it more reliably.

  Such an effect is essential for having a higher pumping capacity.

  On the other hand, as shown in FIG. 11, the concave grooves Gya, Gla, G2a, G3a, and Gxa are symmetric about the Y axis.

  This is symmetrical about the Y axis only in the upper part, and all the remaining grooves Gxa formed in the lower part have the same depth.

  Eventually, all the grooves are formed with a depth of the form shown and described in FIG.

  However, in the present invention, the same result can be obtained by changing the diameter of the concave groove and adjusting the size of the ball seated therein.

  That is, as shown in FIG. 14, the concave groove 231 has a diameter of Mya <M1a <M2a <M3a <Mxa. Are also formed with a diameter of Mxa, the bearing means to be inserted are seated with the same diameter.

  More specifically, the height at which the bearing means such as a ball or a needle pin protrudes from the concave groove varies depending on the diameter of the bearing means.

  Of course, if a ball having the same diameter is inserted into the groove of Mya <M1a <M2a <M3a <Mxa, the height of the ball protruding from the groove having a large diameter should be large.

  That is, the height of the protruding ball is similar to the order of the grooves of Mya <M1a <M2a <M3a <Mxa.

  Even if it carries out like this, this invention does not matter.

  Here, the bearing means 210 has been described a little, but in the present invention, various types of bearing means 210 can be seated in the concave groove 231.

  That is, the bearing means 210 can be a ball or a needle pin.

  Here, a large number of balls are seated in the concave groove 231, and in the case of a needle pin, they are seated in the concave groove 231 in a long shape.

  In practical use of the present invention, in the case of the ball, it is desirable to mount a fluid having a low viscosity, that is, a fluid such as water, and in the case of a needle pin, a fluid such as clay having a high viscosity is pumped. It is desirable to put on when doing.

Further, the rotor of the second actual example that operates in the same manner as the rotor 200 of the first embodiment is shown in FIGS. 15 and 16, and will be described in detail based on these.
That is, the rotor 200 according to the second embodiment of the present invention has a cylindrical shape with a smaller diameter than the inner peripheral surface of the volume chamber 30, and a cylindrical housing 230 having a circular space 260 on the inner peripheral surface. And an eccentric rotating body 220 that is smaller in diameter than the inner peripheral surface of the cylindrical housing 230 and is fitted on the rotary shafts S1 and S2 in an eccentric state, and a large number of concave grooves 271 are provided around the outer peripheral surface. Is formed.

  Further, there is a bearing means 210 that is seated in a number of concave grooves 271 of the eccentric rotating body 220.

  The cylindrical casing 230 and the eccentric rotator 220 are accommodated in the upper and lower volume chambers 39, respectively, and the two cylindrical casings 230 are connected to each other via a partition plate 207 and rotate eccentrically.

  That is, the rotor 200 according to the second embodiment is not different from the rotor 200 according to the first embodiment described above, except that a concave groove is formed on the outer peripheral surface of the eccentric rotating body 220.

  Of course, the bearing means 210 is seated in the concave groove 271 of the eccentric rotator 220, and the bearing means 210 is required to allow the eccentric rotator 220 to rotate more easily inside the cylindrical housing 230. I will provide a.

  Eventually, the rotor 200 of the second embodiment operates in the same manner as the first embodiment and performs the pumping operation.

  Therefore, detailed description is omitted.

  On the other hand, the concave groove 271 formed in the eccentric rotor 220 of the rotor of the second embodiment is formed symmetrically with different depths that gradually become deeper in the order of Fxa <F1a <F2a <F3a <Fya. .

  That is, unlike the first embodiment described above, the concave groove 271 is formed at a constant angle along the outer peripheral surface of the eccentric rotating body 220.

  The concave groove 271 has the deepest Fxa as shown in FIG.

  This means that the Fxa groove located in the 90-degree direction of the eccentric rotating body 220 is deepest.

  Then, the remaining grooves formed at a constant angular interval with each other become shallower in the order of F1a> F2a> F3a> Fya.

  That is, Fxa is deepest and Fya is shallowest.

  However, such a groove is formed with a concave groove 271 at the same depth on the outer peripheral surface of the eccentric rotator 220 so as to be symmetric with respect to the center point of the eccentric rotator 220 (away from the direction of 180 degrees). ing.

  Accordingly, when the circular bearing means 210 is inserted into the concave groove 271, the result is as shown in FIG.

  That is, the protruding height of the bearing means (ball or needle pin) seated in the concave groove Fxa positioned in the 90 o'clock 3 o'clock direction of the eccentric rotating body 220 is the smallest, and the eccentric rotating body 220 of 0 degree The protruding height of the bearing means (ball or needle pin; 210) seated in the concave groove Fya located in the 12 o'clock direction is the highest.

  Hereinafter, an example in which the diameters of the concave groove formed in the eccentric rotating body and the bearing means seated in the concave groove are different and the same effect as that of the above-described embodiment will be described with reference to FIG. .

  That is, the diameter of the concave groove 271 formed in the eccentric rotating body becomes four large in the order of Nya <Nla <N2a <N3a <Nxa, and bearing means of the same diameter is seated in the concave groove. And formed on the outer peripheral surface of the eccentric rotating body so as to be symmetrical in all directions.

  Here, when the diameter of the groove is large, the bearing means having a larger diameter is inserted, so that the height of the protruding bearing means should be increased.

  This has the same contour as the embodiment described above, and the effect is the same.

  Hereinafter, the outline of the eccentric rotating body defined by the bearing means will be described. As shown in FIG. 18, a fairly important concept is produced. However, the bearing means 210, that is, a ball or needle protruding from the concave groove 271. The outline drawn by connecting the outermost points of the pin becomes a high ellipse at the top and bottom.

  An eccentric rotating body 220 having an elliptical outline is fitted on the rotating shaft that rotates at a fixed position in an eccentric state.

  Then, as shown in FIGS. 15 and 18, when the eccentric rotating body 220 is rotated, bearing means (balls or needle pins) inserted mainly into the uppermost concave groove Fya are formed inside the cylindrical casing. Abuts the peripheral surface.

  Thus, when the eccentric rotating body rotates 90 degrees and reaches the position shown in the second drawing of FIG.

  Next, when the eccentric rotating body rotates by 180 degrees and is positioned in the 6 o'clock direction, as shown in the third drawing of FIG. 18, the shallowest groove Fya is pressed. .

  Of course, since the groove of the Fya is at the shallowest position, when the ball or needle pin is formed inside the groove, the highest protruding height is formed. Results in pressing.

  Therefore, as shown in the third drawing of FIG. 18, it serves to securely block the passage below, and produces the effect of maximizing the pumping force of the pump.

  Further, the bearing means 210 according to the second embodiment of the present invention may be a ball or a needle pin as in the first embodiment described above.

  On the other hand, in the present invention, a ball or a needle pin is used as the bearing means 210.

  The interval between the balls and needle pins is preferably determined by the difference between the diameter of the inner circular space 235 formed inside the cylindrical housing 230 and the circular outer peripheral diameter formed by the eccentric rotating body 220.

  That is, FIG. 19 exaggerates the difference in size for explaining the concept, but the diameter of the eccentric rotating body 220 is smaller than the space 235 formed in the cylindrical housing 230. In the state where the uppermost ball and needle pin P are in contact with each other, it rotates along the inner peripheral surface of the cylindrical housing 230, and the next contact portion (contact point) is at the T point as shown. Become.

That is, P and T are in very close positions.
The smaller the diameter of the eccentric rotator 220 is, the closer the portion should be at the contact point.

  On the contrary, as shown in FIG. 20, when the diameter of the eccentric rotator 220 becomes almost equal to the space 235 inside the cylindrical housing 230, the uppermost ball or needle pin P is In the abutting state, the eccentric rotating body 220 rotates along the inner week surface of the cylindrical casing 230, and the next contact portion becomes a point T as indicated by M.

  That is, the distance between P and T is greater than that in FIG.

  Therefore, as the diameter of the eccentric rotating body 220 decreases, the number of balls and needle pins that are required decreases.

  In the present invention, as shown in FIGS. 21 to 29, the volume chamber 30 is preferably formed in a multistage structure.

  That is, 1 to 10 pairs of upper and lower volume chambers 30 in which the rotor 200 of the present invention is built are assembled in a row-like multistage structure.

  This multistage structure means that a plurality of rotors 200 and volume chambers 30 are arranged on the upper and lower rotating shafts.

  More specifically, in the multistage rotary pump according to the present invention, a large number of volume chambers 30 are arranged side by side, and a partition plate is interposed between the volume chambers 30, thereby dividing the volume chambers 30. Is done. The upper rotor 200 and the lower rotor 200 mounted in the volume chamber 30 are fitted on one upper rotating shaft S1 and one lower rotating shaft S2, respectively, and are externally mounted on the upper and lower rotating shafts S1 and S2. The upper rotor 200 and the lower rotor 200 that are fitted and disposed in the respective volume chambers 30 are disposed with a phase difference with respect to each other, and the upper and lower rotary shafts S1 and S2 are connected via a speed reducer. Power is transmitted from the motor, and the upper rotor 200 and the lower rotor 200 are configured as the rotor 200 according to the first and second embodiments of the present invention.

  In the multistage rotary pump according to the present invention configured as described above, the upper rotary shaft S1 and the lower rotary shaft S2 are not subjected to torsional stress as described above. The upper rotor 200 and the lower rotor 200 mounted on S2 are not damaged even when rotated in a state of having a phase difference with respect to each other, and the upper rotating shaft S1 and the lower rotating shaft S2 are rotated at a high speed, The upper rotor 200 and the lower rotor 200 can be operated at high speed.

  21 to 29, the multi-stage rotary pump according to the present invention configured and operated as described above may be provided with manifolds at the inlet BC and the outlet BD of the volume chamber 30. In this case, the mixing ratio of two or more kinds of fluids sucked into the volume chamber 30 can be controlled.

  That is, as shown in FIG. 25, the multi-stage rotary pump according to the present invention configured as described above has a first manifold at the inlet BD of the first, second, and third volume chambers CA, CB, and CC. CQ is connected, and a separate suction pipe CF is connected to the inlet BC of the fourth volume chamber CD.

  This allows the first, second, and third volume chambers CA, CB, and CC to draw the target fluid through the first manifold, while the diluent (water or medicine) is sucked into the fourth volume chamber CD through the suction pipe, By being discharged through the second manifold CT connected to the discharge port BD of each volume chamber 30, the mixing ratio of the target fluid and the diluent discharged through the second manifold CT can be adjusted to be constant. it can.

  As shown in FIG. 26, the multi-stage rotary pump according to the present invention configured as described above has a third manifold DA connected to the inlets of the first and second volume chambers CA and CB, and A separate fourth manifold DB can be connected to the inlets BC of the fourth volume chambers CC and CD.

  A reference symbol CT not described in FIG. 26 is a second manifold attached to the discharge port of the volume chamber.

As shown in FIGS. 27 and 28, the multistage rotary pump has a fifth manifold FA connected to the discharge ports BD of the first, second, and third volume chambers CA, CB, and CC. A separate discharge pipe FB is connected to the CD discharge port, or a sixth manifold GA is connected to the discharge ports BD of the first and second volume chambers, and the third and fourth volume chambers CC and CD discharge ports BD are connected. A seventh manifold GB can also be connected to.

  Thereby, the target fluid discharged from the first, second, third, and fourth volume chambers CA, CB, CC, and CD can be separated into a desired ratio.

  And this invention has mounted | worn with the overload prevention tool 20 like FIG.4, 5, 6, 30 and 31 by connecting the axis | shaft of the rotary motor 10, and a clutch axis | shaft.

  That is, the overload prevention device 20 has a large number of ball grooves 21 formed on the outer peripheral surface at the shaft end of the rotary motor 10, and is formed in the transmission unit 100, and has a housing portion 22 in which the motor shaft 11 is housed. There is a coupler 24 having a plurality of ball insertion holes 23 corresponding to the ball grooves 21 around.

  The coupler 24 is fitted with a synthetic resin material covering 26 that prevents the balls 25 from falling off.

  Therefore, when the ball is inserted into the ball groove 21, the ball is inserted into the ball insertion hole 23, and the outside is covered with the carburing 26, and when the transmission unit 100 is overloaded, the ball 25 removes the carburing 26. The ball is released from the ball groove while pushing in the direction, thereby preventing power transmission.

  The end of the output shaft of the rotary motor is formed in a taper shape, and a number of ball grooves 21 are formed on the outer peripheral surface of the end of the output shaft.

  The coupler 24 is formed with an accommodating portion 22 so that the shaft end of the rotary motor 10 is inserted therein, and the helical gear 12 is provided at the end thereof.

  Of course, a ball insertion hole 23 corresponding to the ball groove 21 is formed in the outer portion of the housing portion 22.

  Accordingly, when the coupler 24 is connected to the output shaft of the rotary motor 10 with the ball inserted in the logarithmic ball insertion hole 23, the ball is seated in the ball groove 21.

  Thereafter, since the carburing 26 is externally fitted to the coupler 24, the ball abuts against the inner peripheral surface of the carburing 26 and does not drop out to the outside, and is firmly seated in the ball groove 21. Maintained.

  Therefore, when the rotary motor 10 rotates, the coupler 24 of the present invention rotates while being firmly connected to the transmission unit 100, and operates the pump of the present invention.

  However, if pebbles or a material with strong hardness is sandwiched between the rotor 200 or the transmission unit 100 of the present invention and an overload is applied to the rotation of the motor, the coupler 24 that connects the motor shaft and the transmission unit can rotate further. Without overload.

  At this time, when the overload becomes large, the ball presses the synthetic resin carburing 26 covering the outer portion outwardly and is detached from the ball groove. By such an action, it is possible to prevent damage to the transmission unit 100 that is frequently generated in the conventional pump.

  That is, in the conventional pump, when an overload as described above is applied, the load is transmitted to the gear crest of the transmission unit 100, resulting in a failure.

  However, in the present invention, such a problem is solved by providing the overload prevention device 20.

It is a figure which shows the rotor part of the conventional general rotary pump. It is a figure which shows the coupling | bonding system of the partition plate and active groove of the rotor part of conventional invention. It is a figure which shows the mode of operation of the rotor for demonstrating the concept of this invention. It is a conceptual diagram explaining the principle which the partition of this invention must be long. It is sectional drawing which shows 1st Example in connection with the transmission unit of this invention. It is sectional drawing which shows 2nd Example regarding the transmission unit of this invention. It is sectional drawing which shows 3rd Example regarding the transmission unit of this invention. It is sectional drawing which shows 4th Example regarding the transmission unit of this invention. It is a figure which shows the operation | movement aspect of the rotor part of this invention. It is a figure which shows the operation | movement aspect of the rotor part of this invention. It is the figure which expanded the rotor part of 1st Example of this invention. It is a figure which shows the mode of the cylindrical housing | casing by 1st Example of the rotor part of this invention. It is a conceptual diagram explaining the action | operation of the rotor part of 1st Example of this invention. It is a figure which shows the other form of the rotor part of 1st Example of this invention. It is the figure which expanded the rotor part of 2nd Example of this invention. It is a figure which shows the mode of the eccentric rotary body by 2nd Example of the rotor part of this invention. It is a figure which shows the other form of 2nd Example of this invention. It is a conceptual diagram explaining the action | operation of the rotor part of 2nd Example of this invention. It is a figure explaining the concept of the installation form of the bearing means of this invention. It is a figure explaining the concept of the installation form of the bearing means of this invention. It is a front view of the pump of the present invention. It is a side view of the two-stage pump of the present invention. It is a side view of the three-stage pump of the present invention. It is a side view of the four-stage pump of the present invention. It is a figure which shows one Embodiment regarding piping of the pump of this invention. It is a figure which shows one Embodiment regarding piping of the pump of this invention. It is a figure which shows one Embodiment regarding piping of the pump of this invention. It is a figure which shows one Embodiment regarding piping of the pump of this invention. It is sectional drawing of the whole four-stage pump of this invention. It is a perspective view which shows the load preventing tool of this invention. It is an end view of the axis | shaft of the rotary motor with which the load preventing tool of this invention was mounted | worn.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10: Rotation (drive) motor 11: Output shaft 20: Overload prevention tool 21: Ball groove 22: Storage part 23: Ball insertion hole 24: Coupler 25: Ball 26: Cover ring 100: Transmission unit 110: Low-speed drive gear 111 : First main driving gear 200: Rotor 220: Eccentric rotating body 230: Cylindrical casing

Claims (17)

In a rotary pump having a drive motor and upper and lower volume chambers and pumping with a rotor and a partition plate rotating along the inner peripheral surface of the volume chamber,
A rotary motor (10) in which an output shaft (11) is eccentric to one side, and an overload preventer (20) having a helical gear (12) is fixed to the shaft end;
A transmission unit (100) fixed to the end of the overload prevention device (20);
Volume chambers (30) at both upper and lower ends in which a rotor (200) that receives the movement of the transmission unit (100) is incorporated;
A rotor (200) having an eccentric rotating body (220) provided with a bearing means (210) that makes a circular motion by a pair of rotating shafts (S1, S2) eccentrically disposed inside the pair of rotors (200); But,
A rotary pump characterized in that the rotational speed of a rotary motor is controlled by a transmission unit (100), and the rotor (200) performs pumping rotation to pump fluid to the outside of the volume chamber (30). The transmission unit (100) fixed to the overload prevention device (20) is:
A low-speed driving gear (110) meshed with a helical gear (12) eccentric to one side and keyed to the rotation shaft (S2) on the other side in the eccentric direction;
A first main driving gear (111) key-locked to the lower rotation shaft (S2) of the low speed driving gear (110);
A second main gear (112) meshing with the first main gear (111) and key-fixed to the rotation shaft (S1) at the other end;
The rotary according to claim 1, wherein the first main driving gear (111) is rotated by the high speed rotation of the low speed driving gear (110), and the second main driving gear (112) meshing with the first main driving gear (111) is rotated to the other side. pump. The transmission unit (100) fixed to the overload prevention device (20) is:
A high-speed driving gear (120) meshed with a helical gear (12) eccentric to one side and key-fixed to the rotating shaft (S1) in the eccentric direction;
A first main driving gear (121) keyed to the lower rotation shaft (S1) of the high speed driving gear (120);
A second main gear (122) meshing with the first main gear (121) and key-fixed to the other rotation shaft (S2);
The multi-end according to claim 1, wherein the first main driving gear (121) is rotated by the high speed rotation of the high speed driving gear (120), and the second main driving gear (122) meshing with the first main driving gear is rotated to the other side. Rotary pump. The transmission unit (100) fixed to the overload prevention device (20) is:
The helical gear (12) eccentric to one side meshes with the first gear (131) fitted on the rotational shaft (S2) on the other side in the eccentric direction, and fixed to the lower stage of the first gear (131). A first auxiliary gear (132) having a smaller diameter than the first gear (131)
A second gear (133) having a long diameter meshed with the first auxiliary gear (132) and used as the rotation shaft (S1) on the other side, and a second gear fixed integrally to the lower stage of the second gear (133) A second auxiliary gear (134) having a smaller diameter than (133);
A third gear (135) having a large diameter, which meshes with the second auxiliary gear (134) and is externally fitted to the rotation shaft (S2) on the other side, and a first gear fixed integrally to the lower stage of the third gear (135). A third auxiliary gear (136) having a smaller diameter than the three gear (135);
A fourth gear (137) having a large diameter that is meshed with the third auxiliary gear (136) and fitted on the other rotation shaft (S1), and a first gear fixed to the lower stage of the fourth gear (137). A fourth auxiliary gear (138) having a diameter smaller than that of the four gear (137);
A fifth gear (139) having a long diameter that meshes with the fourth auxiliary gear (138) and is externally fitted to the rotary shaft (S2) on the other side, and a first gear fixed to the lower stage of the fifth gear (139). A fifth auxiliary gear (140) having a smaller diameter than the five gears (139);
A large-diameter driving gear (144) meshed with the fifth auxiliary gear (140) and fixed to the rotary shaft (S1) on the other side by a key (K);
First and second main driving gears (145, 146) keyed to the pair of rotating shafts (S1, S2) with the same diameter.
The first gear 131 and the first auxiliary gear 132 or the fifth gear 139 and the fifth auxiliary gear 140 have a bearing B when they are coupled to the rotary shafts S1 and S2. Built-in to induce low-speed idling, and by transmitting the rotational force of the driving gear (144), the first and second main driving gears (145, 146) rotate at a low speed and the rotor (200) rotates at a low speed. The multi-end rotary pump according to claim 1. Below the fifth gear (139) and the fifth auxiliary gear (140),
The rotary pump according to claim 4, wherein the sixth to eleventh gears and the auxiliary gear can be inserted and dropped at a low speed. The transmission unit (100) fixed to the overload prevention device 20 is:
The helical gear (12) eccentric to one side meshes with the first gear (150) fitted on the rotation shaft (S2) on the other side in the eccentric direction, and fixed to the lower stage of the first gear (150). A first auxiliary gear (151) having a larger diameter than the first gear (150),
A second gear (152) having a short diameter that meshes with the first auxiliary gear (151) and is externally fitted to the rotation shaft (S1) on the other side, and a second gear (152) integrally fixed to the lower stage. A second auxiliary gear (153) having a larger diameter than the two gears (152);
A third gear (154) with a short diameter that meshes with the second auxiliary gear (153) and is externally fitted to the rotation shaft (S2) on the other side, and a first gear fixed to the lower stage of the third gear (154). A third auxiliary gear (155) having a diameter larger than that of the three gear (154);
A fourth gear (156) having a small diameter, which meshes with the third auxiliary gear (155) and is fitted on the other rotation shaft (S1), and a first gear fixed to the lower stage of the fourth gear (156). A fourth auxiliary gear (157) having a diameter larger than that of the four gear (156);
A small diameter driving gear (158) meshing with the fourth auxiliary gear (157) and keyed to the other rotation shaft (S2);
First and second main driving gears (160, 161) keyed to the pair of rotating shafts (S1, S2) with the same diameter;
The first gear (150) and the first auxiliary gear (151) to the fourth gear (156) and the fourth auxiliary gear (157) have a bearing (B) when coupled to the rotation shafts (S1, S2). Built-in to induce high-speed idling, the first and second main driving gears (160, 161) are rotated by transmission of the rotational force of the driving gear (158), and the rotor (200) is rotated at high speed. The rotary pump according to claim 1. Below the fourth gear (156) and the fourth auxiliary gear (157),
The rotary pump according to claim 6, wherein the fifth to tenth gears and the auxiliary gear can be inserted to increase the speed at high speed. The rotor (200)
A cylindrical casing (230) having a cylindrical shape with a smaller diameter than the inner peripheral surface of the volume chamber (30), having a number of concave grooves (231) on the inner peripheral surface, and having a space (235) ,
An eccentric rotating body (220) having a diameter smaller than the inner peripheral surface of the cylindrical casing (230) and having the rotating shafts (S1, S2) fastened in an eccentric state on one side;
Bearing means (210) inserted into a number of concave grooves (231) of the cylindrical housing (230),
The cylindrical casing (230) and the eccentric rotating body (220) are respectively accommodated in the volume chambers (30) at both the upper and lower ends, and are connected via a partition plate (207) between them, and rotate in an eccentric direction. The rotary pump according to claim 1. The concave groove (231) is
The depth is deeply formed in the order of Gya>Gla>G2a>G3a> Gxa,
9. The rotary pump according to claim 8, wherein the cylindrical casing is divided into upper and lower portions, and a groove having a depth of Gxa is formed in each lower portion. The concave groove (231) is
The diameter is formed with a size of Mya <M1a <M2a <M3a <Mxa, and the lower part which divides the cylindrical housing vertically is formed with the diameter of Mxa, and the inserted bearing means has the same diameter. The rotary pump according to claim 8, wherein the rotary pump is combined with the rotary pump. Said bearing means (210) comprises:
The rotary pump according to claim 8, wherein a ball or a needle pin (218) is used. The rotor (200)
A cylindrical housing (230) having a cylindrical shape with a smaller diameter than the inner peripheral surface of the volume chamber (30) and having a circular space (260) on the inner peripheral surface;
The diameter is smaller than the inner peripheral surface of the cylindrical casing (230), and the rotation shafts (S1, S2) are fastened in an eccentric state on one side, and a number of concave grooves ( 271) an eccentric rotating body (220),
Bearing means (210) seated in a number of concave grooves (271) of the eccentric rotating body (220),
The cylindrical casing (230) and the eccentric rotating body (220) are respectively accommodated in the volume chambers (30) at both upper and lower ends, and both are connected via a partition plate (270), and rotate in an eccentric direction. The rotary pump according to claim 1. The concave groove (271)
The rotary pump according to claim 12, wherein the depth is deeply formed in the order of Fxa>Fla>F2a>F3a> Fya, and is formed in four-way symmetry. The concave groove (271)
The diameter is formed with a size of Nya>N1a>N2a>N3a> Nxa, and bearing means having the same diameter is inserted into the concave groove, and formed on the outer peripheral surface of the eccentric rotating body in a four-way symmetrical form. The rotary pump according to claim 13. Said bearing means (210) comprises:
14. The rotary pump according to claim 13, wherein a ball or a needle pin (218) is used. The volume chambers (30) at both upper and lower ends in which the rotor (200) is built are
The rotary pump according to claim 1, wherein 1 to 10 are arranged in a line. The overload prevention device (20)
A number of ball grooves (21) formed on the outer peripheral surface at the shaft end of the rotary motor (10);
A coupler formed in the transmission unit (100), having a receiving portion (22) for receiving the output shaft (11), and having a plurality of ball insertion holes (23) corresponding to the ball grooves (21) around. (24)
A synthetic resin material covering (26) which is surrounded by the outer peripheral surface of the coupler (24) and prevents the ball (25) from falling off;
When the ball is inserted into the ball groove (21), the ball is inserted into the ball insertion hole (23), and the outside is covered with a carburing (26). When the transmission unit (100) is overloaded, the ball (25) The rotary pump according to claim 1, characterized in that it tears the carburing (26) and stops the transmission of force.

Images