JPS6315479B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to extending the life of a pumping tube in a squeeze pump.

Conventionally, in squeeze pumps used for pumping abrasive materials such as mortar and concrete, the material is pumped from the discharge side to the trapped side due to the pressure difference at the starting point where the preceding squeeze roller releases the trapped material. Countermeasures against tube wear due to backflow were considered to be the biggest issue, and to address this issue, Japanese Patent Publications No. 55-46517, JP-A No. 52-148803, and JP-A No. 55-153883 were published.
Various preloading means have been devised, as shown in Japanese Patent Publication No. 2003-120000, for equalizing the pressures on the discharge side and the confinement side by partially changing the rotational speeds of the leading roller and the trailing roller.

However, the first of these was devised by the inventors of the present application, but in this one, the drive arm and the roller arm only come into contact through the cam part, so the leading roller At the moment when the roller arm is completely separated from the tube, the pressure inside the tube causes the roller arm to be kicked forward, posing the problem that a shock absorbing device is required to prevent this.

In addition, the second method requires a separate hydraulic cylinder drive source, which is a major drawback, and the third method also requires a separate hydraulic cylinder drive source.
In order to preload with a spring force equivalent to the discharge pressure, it is necessary to store more spring force than that, and this additional force is required separately from the tube pressing rotation by the roller, so the overall This has the disadvantage that it requires a large amount of power, resulting in an extremely inefficient pump.

In view of the above-mentioned circumstances, the present invention provides a bearing at the center of one side wall of a cylindrical drum, fixes a sun gear with a bearing at the center of the other side, supports a drive shaft by the bearings on both sides of the cylindrical drum, and supports the drive shaft. Squeeze rollers are rotatably attached to multiple arms rotatably attached to the shaft, and sun gears are meshed with each of the multiple drive arms fixed to the drive shaft, so that the sun gear and the gears have an integer ratio. A planetary gear is provided,
The eccentric shaft of the planetary gear and the shaft of the squeeze roller are respectively pivotally connected by links, and the eccentric shaft of the planetary gear connected to the squeeze roller near the starting point of confinement and release on the discharge side is the center of the planetary gear and the center of the drive shaft. The eccentric shaft of the planetary gear connected to the squeeze roller is located near the straight line connecting the center of the planetary gear and the center of the drive shaft near the closing completion point on the suction side. Each squeeze roller is driven by non-uniform rotation with a phase shift from each other, and the squeeze pump is characterized by being able to pre-pressurize the confinement section before it communicates with the discharge side, and uses a relatively simple configuration. The purpose is to extend the life of the pumping tube inexpensively and efficiently, and to achieve quiet operation.

A detailed description will be given based on the embodiment shown in the figures. For convenience of explanation, the left and right in Fig. 1 are referred to as "front" and "rear," respectively.
The left and right in Figure 3 are referred to as "left" and "right".
Reference numeral 1 denotes a pumping tube made of an elastic material that is fitted in a substantially U-shape along the inner periphery of the cylindrical drum 2 and has nipples 3, 3 inserted therein with both ends protruding an appropriate amount in the tangential direction, and is integral with the cylindrical drum 2. It is fixed to the cylindrical drum 2 with fixing fittings 4, 4 and fastening fittings 5, 5 which are fixed to the guide portion formed in the cylindrical drum 2.

Reference numeral 6 denotes a drive shaft, which is inserted into the center of a large circular hole 7a provided in the center of the cover plate 7 forming the rear wall of the cylindrical drum 2, and its front end is integrally formed with the cylindrical drum 2, as shown in FIG. A bearing 9 is installed on the inner surface of the center of the front wall 2a.
The rear end of the drive shaft 6 projects rearward and outward from the cover plate 7 to form a motor connection portion. 8 is a gear part 8a at the front and rear respectively.
and a sun gear integrally formed with a flange portion 8b, which is rotatably supported on the rear part of the drive shaft 6 via a bearing 10 with the gear portion 8a facing inside the cylindrical drum 2, and the flange portion 8b is They are overlapped with the rear surface of the peripheral portion of the circular hole 7a of the cover plate 7, and are cut on the outer periphery of the flange portion 8b so as to be arranged radially with respect to the center of the drive shaft 6 and extend in a concentric arc shape centered on the center. The sun gear 8 is integrally fixed to the cover plate 7 by inserting bolts 8c into the plurality of elongated holes _8b1 , screwing the tips of the bolts 8c into the cover plate 7, and tightening them.

Reference numerals 11 and 12 denote squeeze roller arms rotatably supported separately via bearings 13 on drive shafts 6 near the side wall 2a, and squeeze rollers 17 are mounted on roller shafts 14 and 15 fixed at their tips via bearings 16, respectively. , 18 are rotatably mounted. 19a,1
9b and 20a, 20b are restoring rollers protruding from the center of the arms 11, 12.

Reference numeral 21 denotes a drive arm keyed onto the drive shaft 6 between the sun gear 8 and the squeeze roller arm 12, and planetary gears 23 having the same number of teeth as the sun gear 8 are connected to the opposing ends via bearings 22, respectively. , 24 are rotatably mounted and meshed with the sun gear 8. Further, the planetary gears 23 and 24 have eccentric shafts 23a and 24 at appropriate eccentric positions on the opposite side of the gears, respectively.
4a protrudes from the link 2 through the bearings 25 and 26.
4 and 28 are pivotally connected to the extended ends of the roller shafts 14 and 15.

Therefore, the relationship between the squeeze rollers 17 and 18 and the planetary gears 23 and 24 is such that when the squeeze rollers 17 and 18 are in the vertical upper position in FIG. 23a or 24a center and drive shaft 6
On the side where the center distance is smaller than the orbital radius of the planetary gear 23 or 24 center, that is, inside the orbit of the planetary gear 23 or 24 centering on the drive shaft 6,
In addition, when the pumping tube 1 is in the vertical lower position, that is, near the complete closing point of the pumping tube 1, the distance between the center of the eccentric shaft 23a or 24a and the center of the drive shaft 6 is the same as that of the planetary gear 2.
They are arranged so as to be located on the side larger than the revolution radius of the center 3 or 24, that is, on the outside of the revolution orbit of the planetary gear 23 or 24 centering on the drive shaft 6, respectively.

Next, the effect will be explained. As the operation starts, the drive arm 21 rotates clockwise as shown by the arrow in FIG.
3 and 24 also revolve around the sun gear 8 while rotating clockwise. Therefore, the squeeze rollers 17 and 18 also revolve in the same direction via the links 27 and 28, but the trailing roller 17 located on the lower side (suction side) in FIG.
Since the center is outside the orbit, the drive arm 2
For the same rotation angle of 1, the leading roller 18 located on the upper side (discharge side) is given a rotation speed that is larger than the average value, and the center of the eccentric shaft 24a is inside the orbit, so the rotation speed is smaller. It will be given to you.

FIG. 3 shows a state slightly rotated from the state shown in FIG. 2, and as is clear from the figure, the squeeze roller 17,
18 are α and β angles, respectively, α>Θ>β
There is a relationship between

Therefore, the trailing roller 17 completes confinement before the leading roller 18 reaches the confinement release start point, and furthermore, within the confinement period, the trailing roller 17 performs confinement at a rotation speed higher than that of the leading roller 18. The pumped material within the section is pressurized.

As a result, even if the preceding roller 18 starts to release the confinement, the pressures on the discharge side and the confinement side are close to each other, so that backflow hardly occurs.

In order to adapt the amount of speed increase from the average value at the closing completion position of the trailing roller to the discharge side use condition and make it equivalent to the discharge pressure, fix it through the arc-shaped long hole _8b1 of the sun gear 8. If you loosen the bolt 8c, adjust the rotation of the sun gear 8, and fix it again, the planetary gear 23,
Eccentric shaft 2 connecting links 27 and 28 to 24
This can be done by changing the phases of 3a and 24a and adjusting the closing and opening start point of the leading roller and the closing completion point of the trailing roller.

Furthermore, if the lengths of the links 27 and 28 are made adjustable, or the eccentric shafts 23a and 24a of the planetary gears 23 and 24 are repositioned using, for example, stud bolts to change the amount of eccentricity, the adjustment range can be further extended. can be expanded.

In addition, by making the drive arm 21 circular and separating the pump chamber and gear chamber by appropriately interposing a sealing member between the drive arm 21 and the inner periphery of the cylindrical drum 2, it is possible to prevent damage to the gear section by the pumped material in the event that the pumping tube ruptures. It can also be prevented.

The above-mentioned embodiment, as best for the usual implementation, has two squeeze rollers 17, 18, an inscribed angle of the pumping tube 1 with respect to the cylindrical drum 2 of approximately 180°, a sun gear 8, a planetary gear 23,
The ratio of the number of teeth with No. 24 was set to 1:1, but in some cases, the inscribed angle may be slightly larger than 180° or
120 to 180 degrees, the number of rollers is 3, and the ratio of the number of teeth is an equal integer ratio of 3:1, and it is also possible to implement it by appropriately combining these.

As detailed above, in the pump of the present invention,
The squeeze rollers are individually rotatable and connected by a link to the eccentric shaft of the planetary gear provided on the drive arm, and the eccentric shaft of the planetary gear connected to the squeeze roller near the closing completion point on the suction side rotates the drive shaft. The eccentric shaft of the planetary gear, which is located outside the orbit around the center planetary gear and connected to the squeeze roller near the starting point of confinement and release on the discharge side, is located inside the orbit around the planetary gear around the drive shaft. By making the rotational speed near the confinement completion point on the suction side an appropriate amount faster than the rotational speed near the confinement release start point on the discharge side, as shown in
By making it possible to prepress the pumped material in the confinement part to a pressure close to the pressure on the discharge side, it eliminates backflow due to differential pressure at the start of confinement release, prevents tube wear and tear in this part, and extends tube life. It is designed to be extended, and because it uses a link connection instead of transmitting rotation through cams or springs as in conventional systems, it is highly efficient despite its simple structure and eliminates vibrations and pulsations caused by backlash. It is possible to perform quiet operation.

[Brief explanation of the drawing]

The drawings show one embodiment of the present invention, and FIG. 1 is a sectional view of FIG. 2, FIG. 2 is a sectional view of FIG. 1, and FIG. 3 is an explanatory diagram of the operation. In the figure, 1 is a pumping tube, 2 is a cylindrical drum, 8 is a sun gear, 11, 12 are squeeze roller arms, 14, 15 are roller shafts, 17, 18 are squeeze rollers, 21 is a drive arm, 23, 24
is a planetary gear, 23a, 24a are eccentric shafts, 27, 2
8 is a link.

Claims (1)

[Scope of Claims] 1. A pumping tube made of an elastic material is fitted inside a cylindrical drum in a substantially U-shape, and the pumping tube is rolled and pressed by the revolution of a plurality of squeeze rollers, wherein the cylindrical drum A bearing is provided in the center of one side wall of the drum, and a sun gear with a bearing is fixed in the center of the other side, a drive shaft is supported by the bearings on both sides of these cylindrical drums, and a plurality of gears are rotatably provided on the drive shaft. a squeeze roller is rotatably attached to each of the arms, and each of the plurality of drive arms fixed to the drive shaft is provided with a planetary gear meshing with the sun gear and having a number of teeth in an integer ratio with the sun gear; The eccentric shafts of these planetary gears and the shaft of the squeeze roller are respectively pivotally connected by links, and the eccentric shaft of the planetary gear connected to the squeeze roller near the starting point of confinement and release on the discharge side is a planetary gear centered on the drive shaft. The eccentric shaft of the planetary gear, which is located inside the center revolution orbit and connected to the squeeze roller near the closing completion point on the suction side, is outside the revolution orbit around the planet gear centering on the drive shaft. A squeeze type pump characterized in that the squeeze rollers are driven by non-uniform rotations with mutually shifted phases, and the confining portion can be preloaded before communicating with the discharge side. 2. The squeeze pump according to claim 1, wherein the ratio of the number of teeth between the sun gear and the planetary gear is 1:1. 3. The squeeze pump according to claim 1, wherein the fixed position of the sun is shifted by an elongated hole so that the positional relationship between the closing completion point and the maximum speed point of the squeeze roller can be changed. 4. The squeeze pump according to claim 1, wherein the drive arm is circular and a sealing member is provided between the drive arm and the cylindrical drum so that the pump chamber and the gear chamber can be partitioned in a liquid-tight manner. 5. The squeeze pump according to claim 1, wherein the length of the link is adjustable. 6. The squeeze pump according to claim 1, wherein the amount of eccentricity of the eccentric shaft of the planetary gear can be changed.