JP6942548B2 - High viscosity fluid pump - Google Patents

Description

The present invention relates to a positive displacement pump that transfers a highly viscous fluid.

Screw pumps and gear pumps are used to pump foods or high-viscosity liquids that are the raw materials for foods. Plunger pumps are not suitable for high-viscosity fluids because the suction and discharge valves cannot operate completely when pumping high-viscosity liquids.

The screw pump uses the kinematic viscosity between the screw surface and the inner surface of the pipe to convey the fluid from one end to the other. In the case of a high-viscosity fluid, there is a limit that the rotation of the screw itself becomes impossible or the transport becomes unstable in some cases.

High-viscosity liquid pumps, which are foods or raw materials for foods, generally have a structure in which a conveyed product adheres to a pump component, and there is a problem that it is difficult to clean the component on which the product adheres. Patent Document 1 states that the arrangement of bearings and the structure of the gear pump are devised to make the pump easier to clean, but it relates to the arrangement of bearings, etc., and is not generally suitable for pumps. The need to clean pump components that come into contact with foodstuffs is a common challenge in foodstuffs or high-viscosity liquid pumps that are raw materials for foodstuffs. Then, as in the example of Patent Document 1, when cleaning the pump, it is necessary to disassemble and clean the product and then reassemble it, and 1) reduction of cleaning maintenance cost and 2) reduction of manufacturing line downtime are required. (Paragraph 0030 of Patent Document 1, second sentence from the end).

In gear pumps, in high-viscosity fluids, sliding between gears often damages the fluid and adversely affects its properties.

Next, the high-viscosity fluid transfer pump also includes a rotary type pump, and a type using a biaxial rotor is disclosed in Non-Patent Document 1. In the pump disclosed in Non-Patent Document 1, a vacuum is created in the suction port of the pump by two rotating rotors, liquid is sucked into the space, and the two rotating rotors are rotated in a non-contact manner by a timing gear. , The fluid of the pump is extruded "continuously" (here, "continuous" is the expression described in the description of the operating principle diagram in the non-patent document) every time the two rotors rotate 180 degrees. (Non-Patent Document 1, operating principle diagram described on the same page). In this configuration, the pulsation is still not suppressed, and the discharge of the pump fluid can be said to be intermittent rather than continuous.

In pumping of high-viscosity fluid, once the rotor is stationary and a certain amount of time elapses, adsorption occurs at the interface between the high-viscosity fluid and the solid, and the difference and change in the properties of the high-viscosity fluid between the stationary state and pumping. This may cause the rotor to stick to or stick to the pump housing. This point is substantially the same as the problem of the screw type pump, and may be a problem unlike the pure plunger type pump. In particular, the adsorption phenomenon has a problem that the generation conditions are complicated and the occurrence has a stochastic element, which makes it difficult to predict.

Special Table 2011-518276 http://www.miuraz.co.jp/product/pump/vrp.html, Miura Co., Ltd. Top Page> Product Information> Pump / Boiler Parts> High Viscosity Liquid Transfer Pump VRP, July 13, 2017

The main subject of the present invention is to transfer the high-viscosity fluid while avoiding alteration and damage of the high-viscosity fluid due to kinematic friction between the pump drive body and the housing.
1. 1. Reduces pump pulsation,
2. Reduce cleaning maintenance costs,
3. 3. Reduction of production line downtime,
It is to provide a high-viscosity fluid pump that realizes the above.

The high-viscosity fluid pump according to the present invention
With a first rotor having a cross section forming four convex curved surfaces;
A second rotor having a cross section forming four concave curved surfaces and arranged parallel to the axial direction of the first rotor;
A set of timing gears that are integrally coupled to the end faces of the first rotor and the second rotor to synchronize the rotations of the first rotor and the second rotor;
A first pump chamber formed coaxially and concentrically with the first rotor, and a second pump chamber formed axially concentrically with the second rotor in parallel with the first pump chamber. A housing portion having a bearing portion capable of rotatably supporting the first rotor and the second rotor;
In a high-viscosity fluid pump containing A high-viscosity fluid pump having a suction port for a high-viscosity fluid on one side perpendicular to the axial direction and a discharge port facing the suction port on the other side in the central portion in the vertical direction of the second rotor. The unit incorporates the first rotor, the second rotor, and the set of timing gears.
The set of timing gears are formed in a recess formed on the inner surface of the front plate provided on the front side portion of the first rotor and the second rotor, and the back side of the first rotor and the second rotor. It is provided inside the inner peripheral part of the recess formed on the inner surface of the back plate provided in the portion.
The bearing portion is provided on the outer surface of the front plate and the outer surface of the back plate, respectively.
A high-viscosity fluid pump characterized in that the inner arc radius of the first pump chamber is formed larger than the inner arc radius of the second pump chamber .

The volume of the space on the fluid inlet side of this pump expands due to the rotation of the rotor, and the volume of the space on the outlet side decreases, and suction / discharge is performed. Carried to the side. That is, as the rotating of the rotor causes the concave-convex curved surface to rotate, the space on the fluid inlet side is expanded to vacuum-suck the high-viscosity fluid from the suction port, and the space surrounded by the arc and the pump interior wall, the convex curved surface and the housing. The chevron rotary chamber surrounded by the inner wall is swiveled around the axis on the first pump chamber side, and the convex curved surface and the rotary chamber surrounded by the housing pump chamber wall are swiveled around the axis, respectively, to the discharge port side. The transfer fluid is swirled and transferred, and the conveyed fluid is discharged to the outside of the discharge port so that the convex curved portion of the first rotor and the concave curved portion of the second rotor mesh and squeeze, and suction, transfer, and discharge are performed by the pump drive body and the housing. It will be completed while avoiding alteration and damage of the high-viscosity fluid due to kinematic-viscous friction between them. The formation and rotation of the plurality of rotary chambers also has the effect of smoothing the pump pulsation and load fluctuation.

Here, the timing gear makes the rotation of each rotor synchronous, but is integrally coupled to the end face of the rotor and is arranged in the flow path of the conveyed liquid. As a result, in the cleaning process after completing the manufacturing process of one lot, cleaning is completed by the same process as cleaning the pump chamber and the flow path, and the timing gear is arranged outside the pump room and outside the flow path of the conveyed liquid. Compared to the conventional method, the advantage is that the disassembly process of the pump chamber components before cleaning and the reassembly process after cleaning can be omitted, the cleaning maintenance cost is reduced, and the production line downtime is shortened. Provide a pump.

In another aspect, grooves may be formed on the two concave surfaces and the convex surfaces so that the surfaces facing each other do not adhere to each other.

When the groove is formed in this way, the effect of increasing the surface distance between the facing surfaces and reducing the kinematic viscosity resistance can be obtained.

When the groove is formed in this way, the surface distance between the facing surfaces is increased by the groove, the formation of the meniscus at rest is hindered, and the static adhesion resistance is reduced.

Before SL engagement portion is constituted by four.

If the meshing portions are composed of four in this way, the meshing portions are formed more densely than in the three cases, the number of uneven curved surfaces is the same, and the gap between the meshing portions is set to the minimum. You can get the effect that is possible.

As described above, according to the present invention, while avoiding alteration and damage of the high-viscosity fluid due to kinematic friction between the pump drive body and the housing,
1. 1. Reduces pump pulsation,
2. Reduce cleaning maintenance costs,
3. 3. Reduction of production line downtime,
It is possible to provide a high-viscosity fluid pump that realizes the above.

It is a disassembled perspective schematic view excluding the rotating shaft inside the housing of the high-viscosity fluid pump 1, which is one embodiment of the high-viscosity fluid pump according to the present invention. It is a perspective schematic view of the housing appearance of the high-viscosity fluid pump 1 which is one Embodiment of the high-viscosity fluid pump which concerns on this invention. It is a vertical sectional view of the center of the suction port and the discharge port which shows the inside of the housing through the housing front plate 10 in the front schematic view of the high-viscosity fluid pump 1 which is one embodiment of the high-viscosity fluid pump according to the present invention. 6 is a front schematic view of a deformable high-viscosity fluid pump 1 in which neither the rotors 20 and 30, which are internal components of the housing, are hatched. The high-viscosity fluid pump 1 in which only the rotor gear structure is drawn through the housing in order to conceptually show the rotor gear structure in the assembled state of the high-viscosity fluid pump 1 according to the embodiment of the high-viscosity fluid pump according to the present invention. It is a side schematic diagram. It is a side perspective schematic diagram conceptually showing the configuration of the rotor and the timing gear which sees through the housing in the assembled state of the high-viscosity fluid pump 100 which is another embodiment of the high-viscosity fluid pump according to the present invention. It is a pump cycle chart figure of the high-viscosity fluid pump 1 which is one Embodiment of the high-viscosity fluid pump which concerns on this invention. It is a side view which permeates through the housing corresponding to the pump cycle of the high-viscosity fluid pump 1, which is one embodiment of the high-viscosity fluid pump according to the present invention.

Hereinafter, one embodiment of the present invention will be described in detail with reference to the accompanying drawings.

<One Embodiment of the high-viscosity fluid pump 1 according to the present invention>
The high-viscosity fluid pump 1 according to the present invention
With the first rotor 20 having a cross section forming the convex curved surface 21;
A second rotor 30 having a cross section forming a concave curved surface 22 and arranged in parallel to the rotor 20 in the axial direction;
Together with the end faces of the rotors 20, 30, for example, with at least a set of timing gears 42, 43 capable of synchronizing the rotations of the rotors 20, 30 coupled by screw fastening;
The first pump chamber 23 and the first pump chamber 23 formed in a substantially cylindrical shape concentric with the first rotor 20 and the axial direction AX are arranged in parallel with the axial direction AX and axially with the second rotor 30. Bearing units 15, 16, 17, 18 having a second pump chamber 33 formed in a substantially concentric cylindrical shape along AX'and capable of rotatably supporting the rotors 20 and 30 (bearing unit 17, in FIG. 1). 18 is not shown) housing 3;
The high-viscosity fluid pump 1 including the above is a plurality of high-viscosity fluid pumps 1 having the same number of concavo-convex surfaces capable of synchronous rotation of the two rotors 20 and 30 facing each other so that the outer edges of the shaft cross-sectional shapes mesh with each other by the timing gears 42 and 43. As shown in FIG. 2, the housing 3 of the high-viscosity fluid pump 1 includes one of the concave-convex curved surface portions 21 and 22 and is axially perpendicular to the central portion of the meshing portions of the two rotors 20 and 30. A high-viscosity fluid pump 1 having a high-viscosity fluid suction port 7 on the side and a discharge port 8 facing the suction port 7 on the other side, wherein the housing 3 is a first rotor 20 and a second rotor. A high-viscosity fluid pump comprising 30 and the timing gears 42 and 43.

Here, the meshes do not necessarily have to come into contact with each other and may be slightly spaced apart. The convex surface portion 21 has an arc-shaped shaft cross section, and a concave surface portion 71 is formed between adjacent convex surface portions 21, and the arc shape of the shaft cross section is 180 ° out of phase with the arc shape of the shaft cross section. The concave surface portion 71 is formed in a shape. The concave surface portion 22 has an arc-shaped shaft cross section that meshes with the concave surface portion 21, and the arc shape of the shaft cross section that meshes with the concave surface portion 71 between adjacent concave surface portions 22. A convex curved portion 72 having an arc-shaped axial cross section that is 180 ° out of phase with the above is formed.

Further, the timing gear may be further provided in the housing 3 with additional timing gears 46, 47 so as to be coupled to both end faces of the rotor so as to hold the rotor on both sides.

The rotor 20 and the rotor 30 shown by the alternate long and short dash line in FIG. 4 are sandwiched between the timing gears 43 and 46 and the timing gears 42 and 47, respectively, and are integrally connected to the rotor 20 and the rotor 30, respectively. Bearing units 15, 16 and 17 are fixedly coupled to the shafts 61 and 62 and fixedly connected to the housing bodies 4 and 5 by means of (not shown), and are screwed to the outer surface of the pump chamber of the front plate 10 and the back plate 9. , 18 constitute a bearing portion and support each rotor 20 and 30 rotatably. Further, the shaft 62 is fixedly connected to the drive shaft of the motor drive mechanism (not shown), but the support form of the shaft is this. It suffices that it is rotatably supported by the housing 3.

<Operation and effect of the present invention shown in the same embodiment>
In the high-viscosity fluid pump 1 according to the present invention, the rotors 20 and 30 ^{rotate around the axes AX and AX'} , and the pump chambers 23 and 33 are formed on the inner surfaces of the upper and lower housing bodies 4 and 5 of the housing portion 3. A plurality of chambers 37, 38 (shown in FIGS. 3 and 7) formed in the pump chamber surrounded by the inner wall surface of the pump, the inner surface of the housing front plate 10, the inner surface of the housing back plate 9, and the inner surface of the housing side plate 51. Is swiveled around the AX axis concentric with the rotating shaft 62 of the rotor 20, and the high-viscosity fluid is pumped.

The action and effect of the high-viscosity fluid pump 1 in the operating state will be described with reference to the transition diagram 7 of each stage of the pump operation. In general, the time-dependent reference of the strokes of FIGS. 7A to 7E is one cycle of a half rotation of a convex portion or a concave portion provided on the rotor, and one cycle is categorized as each stroke. FIG. 6 shows a pump cycle chart S1. Here, the starting point of one pump cycle is defined as when one outer edge boundary of the rotor 20 approaches the inner surface 23 of the pump inward and starts forming a chamber. Therefore, one cycle is from the start of forming the chamber to turning 180 ° around the AX axis concentric with the rotation axis.

The process is classified and explained in the time course as follows.
(1) Pre-transportation stage (first step: S10, FIG. 7 (a))
(2) First transport step (until the first chamber is formed, the second step: S20, FIGS. 7 (b), 7 (c))
(3) Second transport stage (third step: S30, FIG. 7 (d) until the subsequent chamber is formed)
(4) Discharge stage (fourth stroke: S40, FIG. 7 (e))
(5) Repeat from S10 below

As shown in FIG. 7 (a), the transport liquid 200 (the hatching line portion in FIG. 7) is sucked from the suction port 7, and at the same time, the transport liquid is discharged from the discharge port as shown in FIG. 7 (e). Focusing on one transfer lot of the transfer liquid, the transfer is repeated for each chamber by repeating the steps (1) to (5) in which the transfer liquid lot is transferred as the rotor 20 rotates.

That is, the steps (1) to (5) described in parentheses (), S10, S20, S30, and S40 are categorized over time of the rotating machine based on the rotor rotation, and S10 → S20 → S30 →. S40 → S10 corresponds to one cycle of the pump function. In one embodiment shown in FIG. 1, the rotors 20 and 30 have four meshing portions, and one rotation of the rotor repeats four cycles. The discharge amount is distributed in four discharge cycles during one rotation of the rotor, and the amount discharged in one cycle is averaged and smoothed in the swirl region composed of the convex curved portion, and the inner arc of the first pump chamber is arcuate. Assuming that the radius is R and the radius of the inner arc of the second pump is r, the rotation frequency is f, and the discharge amount per time per pump shaft length (hereinafter, also simply referred to as the pump length) H (hereinafter, simply discharge amount). (Also referred to as) may be given by the following equation (1).

The discharge amount H per hour per pump length is leveled according to Eq. (1). If the shape parameters of the concave and convex parts of the rotor meshing portion are the parameters of the discharge amount per hour and they are in a relationship that complements each other almost closely, the discharge amount H per hour per pump length is set with the inner radii of both pumps as parameters. Is in the relationship of equation (1). In particular, when the meshing portion is composed of an even number as in the present embodiment, the corresponding chamber capacities of the chamber on the first pump chamber side and the chamber on the second pump chamber side are always constant, providing a stable discharge amount. Gives the effect of It is difficult to form a meshing form that can be sufficiently complemented by two meshing portions, and if there are three meshing portions, the opening angle of the concave portion of one chamber is approximately 120 °, which is an obtuse angle, so that the inside of the chamber cannot be squeezed. It becomes sufficient, and is insufficient for (4) discharge in the discharge stage (fourth step: S40). If there are four, it is preferable for squeezing and discharging, and a four-meshing portion configuration is preferable. The embodiment discloses four cases as suitable conditions.

If the number of meshed portions is large, the radius r of the inner surface arc of the second pump becomes relatively large when the surface connection of the uneven surface is smoothed. As a result, since the difference between R and r is small, the discharge amount H becomes small according to the equation (1). Therefore, the four meshing portion configurations have an advantage that they are substantially configured to provide the maximum capacity discharge amount.

In the case of a curved surface configuration that uses an arc shape, the chambers 37 and 38 that use the convex curved surface 21 and the like are rapidly separated from the pump interior wall surface toward the center of the radius due to the convex surface, so that the pump inner wall surface and the rotor are generally sufficient. A gap is secured, and the shearing force flows into the high-viscosity fluid, making it difficult for the shearing force to work, minimizing damage and alteration of the high-viscosity fluid. Although a high-viscosity fluid has a high kinematic viscosity coefficient μ, a sufficient clearance can be secured. Therefore, damage and deterioration due to shearing force are minimized by a relaxation action that is proportional to the kinematic viscosity coefficient μ but inversely proportional to the clearance. The effect is obtained.

In the present embodiment, the concave curved surface 22 of the rotor 30 is provided with a groove 36 in the axial direction. The groove 36 maintains the separation between the curved surfaces of the meshing portion, minimizes damage and deterioration due to the shearing force of the high-viscosity fluid, prevents the high-viscosity fluid from adhering to the meshing solid surface at the time of stopping, and by forming a meniscus. It has the effect of preventing adsorption. The groove is preferably about 1 mm, and the direction may be the axial direction or the axial transverse direction. For example, an axial groove 36 may be added as in the present embodiment, and although not shown, the groove is oblique to the axis. It may be provided in the direction or in a herringbone pattern.

In the present embodiment, the convex curved surface 21 and the concave curved surface 22 are engaged with each other in a curved surface configuration using an arc shape. The meshing portion exhibits sufficient sealing performance, and the addition of the groove 36 makes it possible to enhance the sealing effect even if the meshing portions are separated from each other.

The groove may be formed as a groove 35 on the rotor end face facing the housing back plate 9 and the front plate 10. In this configuration, the groove 35 allows the end faces of the rotors 20 and 30 and the housing back plate 9 and the housing front plate 10 to be formed. It keeps a distance from the body, minimizes damage and deterioration due to the shearing force of the high-viscosity fluid, prevents the high-viscosity fluid from sticking to the meshing solid surface when stopped, and has the effect of preventing adsorption by forming a meniscus.

In the present embodiment, the suction port 7 and the discharge port 8 are relative to each other, and the suction port 7 can also be used as a discharge port if the pump rotation direction is reversed. In that case, the discharge port is used. 8 is used as a suction port. Especially at the time of cleaning, the pump chamber is cleaned by operating in this way. When cleaning, since cleaning of the timing gears 42, 43, 46, 47 is built in the housing as in the present invention, it can be performed at the same time as cleaning the inside of the pump, and when it is arranged outside the housing. There is no need to disassemble the housing 3 as described above. The bearing unit is located outside the pump room and does not require cleaning of this part, and can be easily replaced if necessary. Therefore, according to the present invention, it is possible to obtain the effect that the cleaning process can be simplified, the maintenance cost can be reduced, and the downtime of the production line can be shortened.

<Other Examples of High Viscosity Fluid Pumps According to the Present Invention>
FIG. 5 is a schematic perspective view showing an embodiment of another high-viscosity pump 100, showing a configuration of a rotor and a timing gear through which the housing is seen through (the rotating shaft is not shown). In this embodiment, the timing gear and the rotor are integrally cast and molded by the lost wax manufacturing method, and an advantage that precise formation is possible can be obtained. Other components may be similar to the high viscosity pump 1 of the first embodiment.

Although the embodiments according to the present invention have been described above, the embodiments described here are described in considerable detail. However, the applicant has no intention of limiting or limiting the scope of the attached claims to such a detailed description. Further, the present invention is not limited to the embodiment, and the constituent parts of the invention expressed in one embodiment can be adopted in other embodiments, and further, the present invention can be adopted. It can be modified in various ways within the range that does not deviate from the purpose. And, each effect of solving the problem of the invention taken up here is not limited to appearing in one embodiment at the same time, and it is sufficient if at least one of them is expressed to achieve the object of the invention. Yes, those skilled in the art will be able to easily determine. Accordingly, the invention is broadly limited to specific details, each device and method disclosed and described herein, or a combination thereof, examples, and in the spirit of the applicant's general concept of the invention. It is possible to move away from these details without departing from scope.

The present invention is a high-viscosity fluid pump that seals and swirls a high-viscosity fluid in a multi-chamber and exerts almost no shearing force on the high-viscosity fluid. It is suitable for use in the production line.

1,100 High-viscosity fluid pump 3 Housing part 4, 5 Housing body 7 Suction port 8 Discharge port 9 Housing back plate 10 Housing front plate 15, 16, 17, 18 Bearing unit 20 First rotor 21 Convex curved surface 22 Concave Curved surface 23 First pump chamber 27,28 Shaft hole 30 Second rotor 33 Second pump chamber 35,36 Groove 37,38 Chamber 42,43,46,47 Timing gear 61,62 Shaft 71 Concave curved surface 72 Convex Shape aspect 200 Conveyed liquid
AX axis AX ^'axial direction S1 pump cycle S10 first step S20 the second stage S30 third step S40 fourth stroke

Claims (3)

With a first rotor having a cross section forming four convex curved surfaces;
A second rotor having a cross section forming four concave curved surfaces and arranged parallel to the axial direction of the first rotor;
Wherein the first rotor and the second rotor the first being integrally connected to the end face of the rotor and a second set of timing gears to synchronize the rotation of the rotor; and,
A first pump chamber formed coaxially and concentrically with the first rotor, and a second pump chamber formed axially concentrically with the second rotor in parallel with the first pump chamber. A housing portion having a bearing portion capable of rotatably supporting the first rotor and the second rotor;
High viscosity fluid pump comprising, said the first rotor and the second rotor is the set of timing gears meshing with each other is an outer edge of the shaft cross section, and the said housing portion in a side view the first rotor A high-viscosity fluid pump having a suction port for a high-viscosity fluid on one side perpendicular to the axial direction and a discharge port facing the suction port on the other side in the central portion in the vertical direction of the second rotor. The unit incorporates the first rotor, the second rotor, and the set of timing gears.
The set of timing gears, and the first rotor and a second recess formed on the inner surface of the front plate provided on the front side of the rotor, the rear side of the first rotor and the second rotor It is provided inside the inner peripheral part of the recess formed on the inner surface of the back plate provided in the portion .
The bearing portion is provided on the outer surface of the front plate and the outer surface of the back plate, respectively.
A high-viscosity fluid pump characterized in that the inner arc radius of the first pump chamber is formed larger than the inner arc radius of the second pump chamber. The high-viscosity fluid pump according to claim 1, which has grooves on the side surfaces of the first rotor and the second rotor facing the housing portion. The high-viscosity fluid pump according to claim 1 or 2, wherein the set of timing gears includes spur gears.

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