JP2012077679A - Tube rotary pump - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problems that a tube loses its elastic resilience because stress from a roller is concentrated on one and the same portion on the tube and that it is difficult to pump gas or liquid at a constant flow rate over a long time period in a tube rotary pump.SOLUTION: In the tube rotary pump, a mounting angle of a roller to a rotor is inclined. Peripheral walls are provided which are set at angles different from each other and correspond to the angle of the roller, to thereby disperse positions at which the tube is deformed during operation of the pump. Thus, the tube rotary pump is provided which has less decrease in the flow rate and has high reliability, even when continuously operated over a long period.

Description

In the present invention, the fluid in the tube is continuously moved through the closed position of the tube by squeezing the tube with an external roller so that the fluid in the tube is squeezed. After the ironing is completed, the shape of the tube is restored by the elasticity of the tube, the fluid is filled again in the tube, and the liquid in the tube is moved again by the ironing operation described above. The present invention relates to a tube rotary pump for propelling and moving a liquid material in the tube in the direction of the ironing operation of the roller.

Tube rotary pumps are widely used to transport liquids and gases. In particular, when a fluid object dislikes contamination, it is effective for applications in which the fluid object flows inside the tube without directly touching the outside and moves to another container. In other words, the tube rotary pump squeezes the tube, which is the flow path of the fluid, from outside, so that the fluid itself does not directly contact the propulsion device and can move the non-contaminated fluid. Therefore, the tube rotary pump is an infusion pump for injecting an infusion solution or medicinal solution enclosed in a medical bag into the human body through a dosing tube, a pump for color adjustment such as a bio experiment, a pump for toning such as paint, and other fluids. Used in industrial applications that require movement.

FIG. 1 shows a conventional tube rotary pump 100A. The rotation propulsion mechanism necessary for propelling and moving the fluid filling the inside of the tube 10A includes a rotor 20A engaged with the shaft 2A of the motor 1A, and a plurality (two in FIG. 1) around the outer periphery of the rotor 20A. A roller 30A is rotatably attached to a roller rotation shaft 40A. These rotation propulsion mechanisms are attached to the base 9A. On the other hand, a housing 3A is attached to the base support shaft 5A so as to be partially rotatable on the upper portion of the base 9A. The housing 3A is formed with a peripheral wall C constituting a part of the inner surface of the cylinder so as to surround the outer periphery of the rotor 20A. A locking lever 6A is attached to the housing 3A so as to be partially rotatable on the locking lever support shaft 4A, and the tip of the locking lever 6A is locked to a locking lever stop column 7A fixed to the base 9A. . The locking lever 6A is pushed to the outside by a spring 8A housed in a spring storage column hole G formed in the housing 3A. As a result, the tip of the locking lever 6A is engaged with the locking lever stop column 7A. The peripheral wall C formed in the housing 3A keeps a certain separation distance with respect to the roller 30A by the action of the locking lever stop column 7A.

The tube 10A is inserted into a space that is surrounded by the peripheral wall C and the rotation surface D of the rotor 20A and that includes a groove B formed in the rotation peripheral portion of the rotor 20A. A part of the roller 30A protrudes from the periphery of the rotor 20A. Therefore, the roller 30A presses the tube 10A against the peripheral wall C. The gap between the roller 30A and the peripheral wall C is slightly smaller than the thickness when the tube 10A is crushed, that is, the difference between the outer diameter and the inner diameter of the tube 10A, and the rotor 20A is rotated by the motor 1A. The attached roller 30A squeezes the tube 10A through the gap. The tube 10A is housed in the groove B and led out from the tube rotary pump 100A through a tube lead-out groove H formed in the base 9A.

In addition, the tube rotary pump 100A shown in FIG. 1 is transparently shown so that other structural parts can be understood so that the rotor 20A, the roller 30A, and the tube 10A, which are the main parts of the mechanism, can be well understood. However, other parts are not necessarily visible due to the characteristics of the structure itself.

The tube 10A is attached according to the following procedure. That is, when the locking lever 6A is pushed from the outside, the locking lever 6A is released from the locking lever stop column 7A, and the housing 3A opens and closes above the base 9A with the base support shaft 5A as an axis. Thereafter, the tube 10A is attached by bending the tube 10A into a U-shape and assembling it into the groove B and the tube outlet groove H. Thereafter, by pushing the housing 3A into the base 9A, the locking lever 6A engages with the locking lever stop column 7A, and the housing 3A has the bent U-shaped portion inside the housing 3A and the peripheral wall C as the outer periphery. Store in the part. The roller 30A rotates the rotor 20A so that the roller 30A presses the tube 10A against the peripheral wall C, squeezes the tube 10A in the rotation direction of the rotor 20A, and propels and moves the fluid filling the tube 10A.

2A and 2B are schematic views of the conventional tube rotary pump 100A shown in FIG. 1 as viewed from the axial direction of the motor shaft 2A. FIG. 2B particularly shows a state in which the housing 3A is opened. Regarding the components shown in each figure, the same components as those shown in FIG. 1 are denoted by the same reference numerals as those in FIG.

In the conventional tube rotary pump 100A shown in FIGS. 1, 2A, and 2B, the rotor 20A has two rollers 30A, and the peripheral wall C of the housing 3A is approximately 360 degrees / rotation with respect to the rotation of the rotor 20A. 2 = A circumferential angle of about 180 degrees is formed. Realizing this circumferential angle in the housing 3A is a necessary condition that the roller 30A can propel and move the fluid in the squeezing direction without causing a backflow while maintaining the sealing effect of the fluid in the tube 10A. It is. On the other hand, in the case of a tube rotary pump having three rotors 20A, the circumferential wall C needs a circumferential angle of about 360 degrees / 3 = about 120 degrees. Since this circumferential angle is smaller than the tube rotary pump 100A, the housing 3A can be made small in the case of the tube rotary pump having three.

3A and 3B are cross-sectional views of the main part showing a state in which the roller 30A is squeezing the tube 10A in the conventional tube rotary pump 100A. FIG. 3A shows a state where the roller 30A is pressing the tube 10A against the peripheral wall C of the housing 3A. In FIG. 3B, before and after the above state, the roller 30A rotates in accordance with the rotor 20A and changes its position. The roller 30A does not exist in the cross section of the rotor 20A, and the tube 10A is pressed against the peripheral wall C by the roller 30A. Indicates a free state. In this state, the tube 10A returns to the original circular cross-sectional shape even after restoration. Further, the tube 10A is held in the groove B and does not protrude from between the rotor 20A and the peripheral wall C. When two rollers 30A are provided in the rotor 20A, the tube 10A is squeezed twice for each rotation of the rotor 20A, and three or four rollers 30A are provided in the rotor 20A. In this case, the tube is squeezed 3 degrees or 4 degrees for each rotation of the rotor 20A. Then, the pump flow rate is almost determined by (tube cross-sectional area) × (circumferential distance between rollers) × (number of ironing per unit time).

  A pump similar to the conventional tube rotary pump 100A is disclosed in the following patent document.

JP 2003-113882 A JP 2003-254260 A JP 2004-156489 A

The conventional tube rotary pump 100A has a simple structure, and once the number of rotors is determined, the flow rate of the pump can be easily determined by the number of ironing per unit time, that is, the rotational speed of the rotor 20A. Widely used from the aspect. However, it has the following fundamental problems.

The conventional tube rotary pump 100A deforms by crushing the tube 10A with the roller 30A to close the tube 10A, and moves the closed position in the rotation direction of the rotor 20A. Thus, the fluid in the tube 10A is propelled and moved. Therefore, when the tube rotary pump 100A is continuously operated for a long time, the tube 10A undergoes deformation fatigue due to the roller 30A and loses its elastic restoring force, and the cross section of the tube 10A is crushed in the pressing direction F by the roller 30A as shown in FIG. It becomes a flat shape. Then, when the pump flow rate is given by (tube cross-sectional area) × (circumferential distance between rollers) × (number of ironing per unit time), the cross-sectional shape of the tube 10A was circular before continuous use. As a result of continuous use for a long period of time, the cross-section becomes a flat shape with time as shown in FIG. 4, and the pump flow rate gradually decreases. That is, the cross sectional area of the flat circle (ellipse) is smaller than the cross sectional area of the original circular cross section. Further, the tube 10A has a fatigue due to deformation fatigue, and the closing line E of the tube 10A (the bending line along the longitudinal direction formed by both ends of the tube cross section crushed by the roller 30A in the tube 10A) is the most fatigued. Along the tube 10A, it becomes easy to tear. Any deterioration of the tube causes the problem that the tube rotary pump 100A has a problem that the pump flow rate is lowered and the reliability is lowered during long-term operation.

Such a decrease in the pump flow rate can be used only for a short time for the purpose of medical infusion pumps that require a constant flow rate of infusions and pumps that are used for color matching of paints that require liquid volume measurement accuracy. Means. Conversely, long-term use causes problems such as medical safety and poor quality of paint. In addition, the tube rotary pump has a great feature that the liquid or gas to be transported is not directly touched by the propulsion mechanism for transport, so that the liquid or gas to be transported is not contaminated by the pump propulsion mechanism. . However, if the tube 10A is torn due to deformation fatigue and the fluid in the tube 10A is contaminated, a lot of labor and long-time cleaning work will be required to eliminate the contamination on the downstream side of the pump. The economic burden on the user is significant.

Therefore, an object of the present invention is to provide a tube rotary pump that slows down the flat deformation of the tube over time and causes little decrease in pump flow rate even if the tube is continuously operated for a long time. This facilitates mass production of safe medical infusion pumps and high quality paints.

As described above, the tube rotary pump has two or more rollers in the rotor, and the rollers squeeze the tube to propel and move the fluid in the tube. With regard to this structure, in the conventional tube rotary pump, since the roller squeezes the tube at the same position and the same pressing direction in the tube cross section, deformation fatigue of the tube has occurred. As a result, conventional tube rotary pumps have not been able to solve the problems of reduced pump flow rate and reduced reliability.
Therefore,

In order to solve this problem, in the present invention, the progress of deformation fatigue of the tube is suppressed by making the portion of the tube surface different for each roller to have a pump structure. For this reason, as a means for pressing different portions of the tube surface against the peripheral wall for each roller, a plurality of rollers are attached to the rotor by changing the projection position on the rotation axis of the rotor, and thereby the rotor rotates to the tube. Twisting is applied to cause rotation of the tube in the cross section of the tube. Furthermore, in order to positively change the pressing position and the pressing direction of the roller on the tube surface for each roller, a plurality of rollers are attached non-perpendicular to the rotating surface of the rotor, and the peripheral walls facing the rollers are attached to the rotor. A mechanism that forms non-perpendicular to the rotating surface is used. Further, in the present invention, a mechanism that does not cause rotational sliding between the peripheral wall surface and the roller surface is used by making the cross section of the rotation axis of the roller trapezoidal, that is, by making the peripheral surface of the roller a truncated cone surface.

In the tube rotary pump according to the present invention, specifically, the following structure is disclosed as means for solving the conventional problems.

Specifically, the tube rotary pump according to claim 1 has a basic structure and a characteristic structure. The basic structure is as follows. The housing which comprises a pump main body contains the rotating inner surface which is a surrounding wall where a rotor and a roller which face a tube and a tube face each other in the inside. A motor is mounted in the approximate center of the housing, and the rotation axis of the motor and the axis of the rotor are coincident, and the rotor is engaged with the shaft of the motor. The rotor is driven to rotate through the shaft. A groove is formed around the rotor, and two or more rollers are rotatably mounted in the groove, thereby constituting a rotor mechanism. When the tube is positioned between the peripheral wall provided in the housing and the roller, and the rotor is driven to rotate by the motor, the roller presses the tube against the peripheral wall and, as a result, the rotor fills the tube. The fluid is propelled and moved in the direction of rotation.

In addition to this, the present invention has the following characteristic structure. The characteristic structure is that all or a part of the two or more rollers are located at different projection positions with respect to the rotation axis and around the rotor, and are not in relation to the rotation surface of the rotor. It is attached to its rotating surface at a right angle. The housing has a rotating inner surface formed around the rotation axis and facing each of the peripheral surfaces of the two or more rollers, and the two or more rollers have a rotating inner surface between the peripheral surface and the rotating inner surface. Guide means for guiding the tube is formed in the rotor, and the fluid in the tube is propelled and moved by the peripheral surface and the rotating inner surface of the roller when the rotor rotates. It is the structure of a rotary pump.

If the structure related to the arrangement of the rollers is adopted for the rotor, the rollers are provided at different projection positions with respect to the rotation axis direction of the rotor. Arise. In addition to this, the direction in which the tube is pressed against the rotating inner surface provided on the housing differs depending on the individual rollers. Owing to these two effects, the blocking lines formed by concentrated deformation fatigue appearing on the tube by squeezing the tube are distributed and formed at different positions on the tube cross section. Therefore, the occurrence of flat deformation over time of the tube becomes slow, and as a result, the occurrence of flat deformation over time of the tube is slowed down, and even if the continuous operation is continued for a long time, the pump flow rate does not decrease and is highly reliable. A rotary pump is realized. In order to realize such an ironing operation of the tube, in the present invention, guide means for guiding the tube between the roller and the rotating inner surface is formed on the rotor. Such guiding means ensures the above-mentioned ironing operation.

Further, the present invention according to claim 2 discloses an effective solution means by the newly invented characteristic structure in addition to the same structure as the basic structure. Since the basic structure overlaps, a new characteristic structure will be described below.

That is, in the housing and the two or more rollers constituting the basic structure, the two or more rollers have different projection positions with respect to the rotation axis direction of the housing and around the rotor. All or some of the two or more rollers have a non-cylindrical peripheral surface on the peripheral surface of the roller, and the housing is centered on the rotation axis and faces the peripheral surfaces of the two or more rollers, respectively. A rotating inner surface is formed, and guide means for guiding the tube is formed between the peripheral surface of the two or more rollers and the inner rotating surface, and the rotor is rotated. The tube rotary pump structure is characterized in that the fluid in the tube is propelled and moved by the peripheral surface and the rotating inner surface of the roller.

Further, the invention according to claim 2 is characterized in that the peripheral surface of the roller is a non-cylindrical peripheral surface as compared with the invention according to claim 1. Thereby, although the effect which produces the twist of a tube is the same, it differs in the point which makes the roller the non-cylindrical peripheral surface, ie, a truncated cone surface, as a means to produce | generate the effect from which the direction of the tube pressing differs. By combining these plural inventions, the solution of the problem of realizing a tube rotary pump in which the occurrence of flat deformation over time of the tube is slowed down and the pump flow rate decreases little even if it is operated continuously for a long time. 1 has the same effect. The invention according to claims 1 and 2 greatly expands the degree of freedom of the structure and design of the pump for the purpose of achieving the common effect of the present invention.

Furthermore, in the present invention according to claim 3, in the tube rotary pump according to the inventions of claims 1 and 2, two or more independent pump operations can be performed by simultaneously squeezing two or more tubes. The structure to be realized is disclosed. That is, in the tube rotary pump according to claims 1 and 2, one guide means, a pair of the two or more rollers corresponding thereto, and a set of rotating inner surfaces facing the peripheral surfaces of the two or more rollers, respectively. In combination with each other to realize the squeezing operation of the tube. In the present invention, these are configured as a set in which two or more are connected with the same rotation axis as the rotation axis. A structure of a rotary pump is disclosed.

With such a structure, a tube rotary pump having a plurality of channels can be easily realized. In addition, since the operations of the pumps related to a plurality of channels are synchronized, a plurality of fluid supply channels that can ensure quantitativeness without adjustment by making use of the quantitativeness and reliability in long-time continuous operation, which is an advantage of the present invention. Can be configured.

Furthermore, the invention according to claim 4 discloses a tube rotary pump according to the invention according to any one of claims 1 to 3, wherein the tube guide means is a groove provided in the rotor. For this reason, it becomes the structure which provided the said guide means integrally with the rotor, and can comprise a highly reliable guide means.

Furthermore, in the invention described in claim 5, in the invention described in claim 4, a projecting portion that protrudes from the inner side surface of the groove is used as the guide means. Thereby, the contact area with the tube is not the entire surface of the groove but the surface of these convex portions, so that the contact area between the guide means and the tube is dramatically reduced. For this reason, it becomes possible to reduce the load of the motor connected to the rotor and to save power in the operation of the entire tube rotary pump.

The invention described in claim 6 discloses that the roller according to claim 2 in which the peripheral surface is a non-cylindrical peripheral surface has a truncated cone shape. Thereby, the effect that the rotation of the roller rotating with the rotation of the rotor becomes smooth can be improved.

Diagram showing the structure of a conventional tube rotary pump Front view of conventional tube rotary pump Front view of the conventional tube rotary pump with the housing opened Sectional view of the main part of a conventional tube rotary pump Sectional view of the main part of a conventional tube rotary pump The figure which shows the section after deformation fatigue of the conventional tube Overall configuration diagram of tube rotary pump in the first embodiment Sectional drawing of the principal part in 1st Example Sectional drawing of the principal part in 1st Example Sectional drawing of the principal part in 1st Example The figure which shows the cross section after the tube deformation | transformation fatigue in 1st Example. Perspective perspective external view of the rotor of the second embodiment Overall configuration diagram of tube rotary pump in the third embodiment Perspective perspective external view of a third embodiment Side view of main part of third embodiment Development view of rotor showing roller arrangement in the fourth embodiment Perspective perspective view of essential parts of the fifth embodiment Side view of main part of fifth embodiment Side view of main part of sixth embodiment Side view of main part of seventh embodiment Side view of main parts of eighth embodiment Side view of main parts of ninth embodiment Side view of main part of 10th embodiment Side view of main part of 11th embodiment Side view of main part of 12th embodiment

Examples according to the present invention will be described below with reference to FIGS. In addition, in each figure after FIG. 6A, description is abbreviate | omitted about the overlapping part in another figure, etc., and the same code | symbol, However In principle, it is the same as the corresponding overlapping part and the corresponding same code | symbol. is there.

FIG. 5 shows an overall configuration diagram of the tube rotary pump 101A according to the first embodiment of the present invention. Here, components that are essentially the same as those of the conventional invention described in the background art are given the same reference numerals. That is, the rotation propulsion mechanism includes a rotor 21A engaged with the motor shaft 2A of the motor 1A, and two cylindrical rollers 31A around the rotor 21A, which are freely attached to the roller rotation shaft 41A. The mechanism is attached to the base 9A. On the other hand, a housing 3B is attached to the base 9A via a base support shaft 5A so as to be partially rotatable. In the housing 3B, peripheral walls C1, C2, and C3 (see FIG. 6A) are formed so as to surround the outer periphery of the rotor 21A. A locking lever 6A is attached to the housing 3B so as to be partially rotatable on the locking lever support shaft 4A, and the tip of the locking lever 6A is locked to a locking lever stop column 7A fixed to the base 9A. . The locking lever 6A is pushed to the outside by a spring 8A housed in a spring storage column hole G formed in the housing 3B. As a result, the tip of the locking lever 6A is engaged with the locking lever stop column 7A. . By the action of the locking lever 6A, the peripheral wall formed in the housing 3B can maintain a constant separation distance with respect to the roller 31A.

As one of the features of the present invention, the roller 31A is attached not at a right angle to the rotation surface of the rotor 21A but at an acute angle, and a plurality of rollers 31A are provided with respect to the rotor 21A, and around the rotation axis of the rotor 21A. The peripheral surface of each roller 31A is in a different position. In the first embodiment shown here, an example in which two rollers 31A are provided is shown. The two rollers 31A are rotatably attached to a groove B1 provided around the rotor 21A. On the other hand, unlike the conventional tube rotary pump 100A, the two peripheral walls C1 and C3 corresponding to the mounting angles of the two rollers 31A shown in FIG. 6A below function as the peripheral walls related to the pump operation in this embodiment. In this embodiment, the groove B1 is a groove that connects the two rollers 31A around the rotor 21A. For this reason, the groove | channel B1 becomes a guide means of the tube 10A corresponding to rotation of the rotor 21A. The tube 10A is led out from the tube outlet H where the tube rotary pump 101A is formed.

6A, FIG. 6B, and FIG. 6C show the cross section of the principal part in 1st Example. All of them show schematic views showing relative positions of the roller 31A, the rotor 21A, and the housing 3B in FIG. These drawings show the relationship between the two rollers 31A and the peripheral walls C1, C2, and C3. That is, the tube 10A remains in the space formed between the roller 31A or the groove B1 with the peripheral walls C1, C2, and C3 as the outer periphery. As the rotor 31A rotates, the roller 31A presses the tube 10A against the peripheral wall C1 and the other roller 31A presses the tube 10A against the peripheral wall C3. When the rotor 21A rotates, the two rollers 31A squeeze the tube 10A to propel and move the fluid filling the tube 10A. The tube 10A is accommodated in the groove B1. The tube 10A is squeezed in different pressing directions by the two rollers 31A and the corresponding peripheral walls C1 and C3.

FIG. 6A shows a schematic cross-sectional view of a state in which the two rollers 31A are pressing the tube 10A against the peripheral walls C1 and C3. Since the two rollers 31A are provided in the groove B1 formed so as to face each other with an inclination angle rather than a right angle with respect to the rotation surface of the rotor 21A, the upper and lower rollers 31A push the tube 10A. The directions are different from each other by about 180 degrees.

FIG. 6B shows a schematic cross-sectional view of a state in which the rotor 21A is rotated 90 degrees compared to the rotor 21A shown in FIG. 6A. In this case, the position of the roller 31A changes according to the rotation of the rotor 21A, and the tube 10A shows a free state in which it is not pressed against the peripheral walls C1 and C3. The tube 10A is stored in the groove B1. In addition, the tube 10A returns to the original circular cross-sectional shape even when restored by the elasticity of the material.

FIG. 6C shows a schematic cross-sectional view of the state in which the rotor 21A is further rotated 90 degrees from FIG. 6B. In this case, the position of the roller 31A changes according to the rotation of the rotor 21A, the roller 31A on the upper side of the drawing presses the tube 10A against the peripheral wall C3, and the roller 31A on the lower side of the drawing similarly presses the tube 10A against the peripheral wall C1. ing. In FIG. 6A, the upper roller 31A pushes the tube 10A in the diagonally upper left direction to close it, but in FIG. 6C, the upper roller 31A pushes the tube 10A in the obliquely upper right direction rotated about 90 degrees to close it. On the other hand, each lower roller 31A shown in FIGS. 6A and 6C pushes the tube 10A in the direction rotated about 90 degrees relative to each other to close the tube 10A.

In this embodiment, when the rotor 21A rotates, the one roller 31A deforms by crushing the tube 10A with the peripheral wall C1 to close the tube 10A, and moves the closed position in the rotation direction of the rotor 21A. Similarly, the other roller 31A deforms by crushing the tube 10A with the peripheral wall C3 to close the tube 10A, and moves the closed position in the rotation direction of the rotor 21A. The principle of the tube rotary pump 101A of the present application is to move the fluid in the tube 10A by such an operation.

The operation will be described in more detail. When the roller 31A is in FIGS. 6A and 6C, the position where the tube 10A is deformed is different. That is, the rotor 21A rotates, the upper roller 31A rotates to the near side, the lower roller 31A rotates to the heel side, and the peripheral walls C1 and C3 are on the near side. Therefore, in FIG. By rotating, the tube 10A is deformed and closed, and the fluid inside is moved. In this case, the blockage of the tube 10A draws a locus of a pair of blockage lines E1 shown in FIG. After the rotor 21A rotates through 180 degrees, the roller 31A comes to the upper part of FIG. 6C. Therefore, when the rotor 21A rotates over the next 180 degrees, the roller 31A crushes and deforms the other part of the tube 10A to close it, and the rotor 21A moves in the rotation direction over the 180 degrees. By doing so, the fluid in the tube 10A is moved. In this case, the occlusion of the tube 10A draws a trajectory of the pair of occlusion lines E2.

In the former rotation of 180 degrees of the rotor 21A and the latter rotation of 180 degrees, the tube 10A accommodated in the groove B1 is rubbed by different peripheral walls C1 and C3 from different angles by the two rollers 31A. . In other words, the closing line E1 and the closing line E2 are at different positions on the surface of the tube 10A as shown in FIG. The change in the position is originally caused by twisting of the tube 10A in the groove B1 with respect to the rotating surface of the rotor 21A. In this embodiment, however, the position of the roller 31A is greatly changed due to the difference in the mounting angle of the roller 31A. It will be. This is because the pressing direction of the roller 31A against the tube 10A is different. For this reason, as shown in FIG. 7, the trajectory of deformation fatigue of the tube 10A is distributed into two, the closing line E1 and the closing line E2, and the fatigue of the tube 10A is halved. Therefore, the plastic deformation of the tube 10A due to deformation fatigue becomes slow, and the original tube cross-sectional shape can be maintained for a long time. Due to such effects, the structure described in the present embodiment is less likely to decrease the pump flow rate even when operated for a long time. Therefore, in the first embodiment of the present invention, it is possible to more easily maintain the safety improvement of the medical infusion pump and the mass production of high quality paint.

FIG. 8 shows a second embodiment. Here, the rotor 21A in the first embodiment is replaced with a rotor 21B. That is, the two rollers 31A are provided with one bearing in a support portion L provided in a groove B1 formed around the rotor 21B, and supported by a roller rotary shaft 41A attached thereto, A guide portion J is provided so that the tube 10A (not shown) is pressed against the peripheral walls C1 and C3 by these rollers 31A and is rubbed by being freely attached to the groove B1. Further, unlike the structure shown in FIGS. 5A and 5B, the guide portion J indicated by hatching is used as a tube guiding means corresponding to the rotation of the rotor 21B. In the second embodiment, the groove B1 is entirely formed with respect to the width around the rotor 21B while maintaining the same operation, function, and effect as in the first embodiment. For this reason, it can be set as the structure which improved the versatility which can respond to the various tubes from which a diameter differs with one type of rotor 21B.

From the same technical point of view as in the first and second embodiments, a structure in which a third roller is provided at the mounting position in the rotor 21A corresponding to the peripheral wall C2 can be used (referred to as a modified embodiment). . In this case, the tube is squeezed between the peripheral walls C1, C2, and C3 and each roller. Further, by using this structure, the circumference of the peripheral wall can be set to about 360 degrees / 3 = 120 degrees, and the housing 3B can be downsized.

FIG. 9 shows an overall perspective view of the tube rotary pump 102A in the third embodiment. The present embodiment has essentially the same structure as the first embodiment, but the roller 32A has a truncated cone shape instead of a cylindrical shape. For this reason, the roller 32A can smoothly rotate the tube 10A more smoothly, and the power consumption of the motor 1A can be reduced by reducing the rotational load of the rotor 22A.

10A and 10B respectively show an external perspective view and a side sectional view of a rotor 22A that is a main part of the third embodiment. The structure of this embodiment is basically the same as that of the first embodiment, except that the roller 32A has a truncated cone surface whose peripheral surface is a non-cylindrical peripheral surface. That is, in the third embodiment, the roller 32A has a truncated cone shape. Further, regarding the truncated cone-shaped roller 32A, the ratio of the diameters at both ends of the truncated cone is substantially the same as the ratio of the rotation radius of the rotor 22A from the rotation axis of the rotor 22A to each end of the truncated cone. Yes. Such a dimensional distribution of the diameter of the roller 32A realizes a structure in which no rotational slip occurs between the surfaces of the peripheral walls C1 and C3 and the rotating surface of the roller 32A. That is, the two rollers 32A have a structure that does not slip due to rotation with respect to the facing surfaces of the peripheral walls C1 and C3, and the rotating operation of the rotor 22A in a state where the tube is attached can be made smooth. . In the present embodiment, as in the first embodiment, two rollers 32A are rotatably attached to a groove B1 provided around the rotor 22A. In this embodiment, the groove B1 serves as a positive guide means for the tube against the rotation of the rotor 22A.

In the third embodiment, the third roller 31A corresponding to the peripheral wall C2 can be provided at the mounting position in the rotor 22A as in the first and second embodiments. FIG. 10C shows a fourth embodiment in which such a third roller 31A is provided. Here, FIG. 10C shows the development of the arrangement of the rollers 31A and 32A provided in the groove B1 of the rotor 22A. The two rollers 32A have a frustoconical shape to oppose the peripheral walls C1 and C3, and the roller 31A opposes the peripheral wall C2 perpendicular to the rotation surface of the rotor 22A, so that the rotation surfaces are cylindrical surfaces. is there. As can be seen from the development view of FIG. 10C, in the development view of the rotor 22A having three rollers, the two rollers 32A and the one roller 31A are arranged at equal intervals in the groove B1. As in the case of the structure in which the three rollers 31A of the second embodiment are provided, the circumference of the peripheral wall (not shown) can be set to about 360 degrees / 3 = 120 degrees, and the housing 3B can be downsized. It becomes possible.

11A and 11B show an external perspective view and a side view of a rotor 23A according to a fifth embodiment of the present invention. The structure of this embodiment is basically the same as that of the third embodiment. The difference is that the width of the groove B1 is larger than the diameter of the tube 10A, and the surface of the protrusion protrudes from the inner surface of the groove B1. The structure which formed the guide fin K which is a part is mentioned. By using such a structure, it becomes possible to make the contour of the guide fin K function as the guide means of the tube 10A. Specifically, guide fins K are formed at intervals of a certain rotation angle of the rotor 23A on both side surfaces and the bottom surface of the groove B1 shown in FIG. 11A. For this reason, the tube 10A comes into contact with the inside of the groove B1 serving as the guiding means, so that the friction between the tube 10A and the rotor 23A can be reduced. In addition, in the structure in the present embodiment, the load of the motor 1A is reduced by the reduction of the friction, so that an effect of power saving is also obtained. FIG. 11C shows a sixth embodiment in which the guide fins K have other shapes. In this embodiment, the guide fin K is formed only on the side portion of the groove B6. Even in this case, an equivalent power saving effect can be obtained.

In the first to sixth embodiments and the modified embodiments, the rotors 21A, 21B, 22A, and 23A are formed with only one channel for guiding the tube 10A. In this case, since the two rollers 31A and the two rollers 32A have different attachment angles with respect to the rotation surfaces of the rotors 21A, 21B, 22A and 23A, the motor shaft 2A is rotated with the rotation of the rotors 21A, 21B, 22A and 23A. On the other hand, a force parallel to the rotation axis direction is applied. Such a force may cause a motor rotating cage (not shown), which is a component of the motor 1A, to generate strong friction with the receiving motor bearing (not shown) in the direction of the motor shaft 2A, or to apply an uneven load to the motor bearing. Yes. Therefore, when two or more of these rotors 21A, 21B, 22A, 23A are attached to the motor shaft 2A to form a multi-channel tube rotary pump of two channels or more, the above-mentioned friction and uneven load are further increased. As a result, the life of the motor 1A (not shown) is remarkably shortened.

As a method for solving this problem, there is a configuration of a mechanism for attaching the rotors 21A, 21B, 22A and 23A to the mirror surface with respect to the rotation surface. As an example of this configuration, FIGS. 12A to 12C show seventh to ninth embodiments. That is, in the seventh to ninth embodiments, the rotors 22A and 23A according to the third embodiment, the fifth embodiment, and the sixth embodiment are respectively mirrored with respect to the rotation surface of the motor shaft 2A. Thus, the rotor 24A is arranged in two series. By using this embodiment, it is possible to prevent the shortening of the life of the motor 1A (not shown) described above.

That is, instead of the rotors 22A and 23A, the rotor 24A is formed so that the groove B1 is a mirror image target with respect to the rotation surface, and the roller 32A is also a mirror image target. On the other hand, although not shown, the peripheral walls C1 and C3 are formed so as to have a plane parallel to the plane of rotation against the rotor 24A. Therefore, in the force with which the roller 32A closes the tube 10A, the force in the direction of the motor shaft 2A has the opposite direction and the same magnitude, and the forces in the direction of the motor shaft 2A cancel each other. As a result, the force parallel to the rotation axis direction of the motor shaft 2A cancels out, and the rotor 24A does not apply the force in the direction of pushing out the motor bearing. Therefore, the life of the motor is not significantly shortened. In such a configuration, the same effect can be obtained by making the rotor in the second embodiment double.

Further, the two rotors 24A are not completely mirror images of the two grooves B1 and the rollers 32A, and even if the grooves B1 and the rollers 32A are slightly displaced at the rotation angle with respect to the rotation surface of the rotor 24A, the motor shaft The force parallel to the rotation axis direction applied to 2A is considerably reduced. Even if the deviation on the rotating surface is 90 degrees, the maximum force parallel to the motor shaft 2A in the direction of the rotation axis is the same as in the case of the series of rotors 22A and 23A. In other words, this displacement on the rotation plane is effective up to 90 degrees from the mirror image object.

Since the seventh to ninth embodiments use the two rotors 24A, the fluid in the tubes 10A can be propelled and moved simultaneously for two tubes 10A (not shown). If necessary, by attaching a rotor adopting a configuration of three or more stations, the fluid in the tubes can be propelled and moved for the number of tubes 10A corresponding to the number of the rotors.

In the seventh to ninth embodiments, since the rotor 24A is doubled as a whole, the housing 3B having a peripheral wall facing the rotor 24A increases in the direction of the motor shaft 2A according to the number of the tubes 10A. As means for solving such an increase in the size of the housing 3B, FIGS. 13A to 13C show tenth to twelfth embodiments.

In the tenth to twelfth embodiments, the two grooves B1 are formed on the rotating peripheral surface of the rotor 25A so as to have the same meandering. In attaching the two rollers 32A, the same effects as those of the seventh to ninth embodiments can be obtained. That is, since the mounting angles of the two rollers 32A with respect to the rotation surface of the rotor 25A are different, the force in the direction of the motor shaft 2A in the direction of closing the two rollers 32A tube 10A (not shown) with the rotation of the rotor 25A. The forces are opposite and have the same magnitude, so they cancel each other. As a result, the force parallel to the rotation axis direction of the motor shaft 2A cancels out, and the rotating cage of the motor 1A (not shown) does not give a force in the direction of pushing out the motor bearing (not shown). As a result, the effect of avoiding the remarkably shortening of the life of the motor 1A is the same as that of the seventh to ninth embodiments.

In Examples 10 to 12, a two-channel tube rotary pump is formed. On the other hand, the rotor 25A is 1.5 times as long as the direction of the motor shaft 2A even when compared with the third and sixth embodiments. In general, assuming that the number of channels is N, the ratio of the size of the rotor 25A to the direction of the motor shaft 2A relative to the direction of the motor shaft 2A in the third to sixth embodiments is 0. 5 + 0.5N. Therefore, as compared with the seventh to ninth embodiments, the increase in the dimension of the housing 3B relative to the size of the rotor 25A in the direction of the motor shaft 2A can be suppressed, and the problem of the increase in dimension can be solved.

In the tenth to twelfth embodiments, the rotational angle of the groove B1 and the rotation surface of the rotor 25A of the roller 32A may be slightly shifted for the same reason as in the seventh to ninth embodiments. In the seventh to twelfth embodiments, a cylindrical roller 31A may be used instead of the truncated cone roller 32A.

In the seventh to twelfth embodiments described above, the rotor 24A or 25A provided with the groove B1 as the guiding means and the two or more rollers 32A to 31A, and the rollers 32A to 31A included in the rotor 24A or 25A are supported. Specifically, there is disclosed a tube rotary pump in which two sets of peripheral walls C1 to C3 as rotating inner surfaces provided in the housing 3B are connected to the same rotation axis, and a tube is provided in the groove B1 to be operated. ing.

On the other hand, not only when the above-described two sets are connected to the same rotational axis, but also when three or more sets are connected to the same rotational axis. With these structures, a tube rotary pump having three or more channels can be configured.

Further, in the seventh to twelfth embodiments, the two rollers 32A are composed of two rollers 32A having a truncated cone shape and one roller 31A having a cylindrical shape as in the fourth embodiment. It is also good.

The present invention is not limited to the above-described embodiments as they are, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. In addition, various inventions can be formed by appropriately combining a plurality of components disclosed in the embodiment. In addition, by removing some constituent elements from all the constituent elements shown in the embodiment, the invention having the same effect as the above-described embodiment can be obtained. Furthermore, the effects described in the above-described examples can be obtained even if the constituent elements over different embodiments are appropriately combined. In addition, a known technical element may be added to an appropriate combination of a plurality of constituent elements disclosed in the above embodiment to obtain an effect similar to that of the above embodiment.

1A Motor 2A Motor shaft 3A, 3B Housing 4A Locking lever support shaft 5A Base support shaft 6A Locking lever 7A Locking lever stop column 8A Spring 9A Tube 10A Tube 20A, 21A, 21B, 22A, 23A, 24A, 25A, rotation Child 30A, 31A, 32A Roller 40A, 41A Roller rotating shaft 100A Conventional tube rotary pump 101A, 102A Tube rotary pump C, C1, C2, C3 Peripheral wall B, B1 Groove D Rotating surface E, E1, E2 Blocking line F Pushing direction G Spring storage column hole H Tube outlet groove L Support part J Guide part K Guide fin

Claims (6)

A housing;
A rotor that rotates about a rotation axis in the housing;
A motor whose rotational axis matches along the rotational axis;
A shaft that transmits the rotation of the motor to the rotor;
Composed of
The rotor includes a groove formed around the rotor engaged with the shaft, and two or more rollers that are freely mounted in the groove. The housing and the roller In the tube rotary pump in which the tube is positioned between and the rotor is driven to rotate by the motor so that the roller is ironed and the fluid in the tube is propelled and moved.
All or a part of the two or more rollers are located at different projection positions with respect to the rotation axis and around the rotor, and are attached to the rotation surface of the rotor at a non-right angle.
The housing has a rotation inner surface formed around the rotation axis and facing the peripheral surfaces of the two or more rollers, respectively.
Guide means for guiding the tube is formed between the peripheral surface of the two or more rollers and the rotating inner surface, and the rotor is rotated by the peripheral surface of the roller and the rotating inner surface when the rotor rotates. A tube rotary pump characterized by propelling and moving a fluid in a tube. A housing;
A rotor that rotates about a rotation axis in the housing;
A motor whose rotational axis matches along the rotational axis;
A shaft that transmits the rotation of the motor to the rotor;
Composed of
The rotor includes a groove formed around the rotor engaged with the shaft, and two or more rollers that are freely mounted in the groove. The housing and the roller In the tube rotary pump in which the tube is positioned between and the rotor is driven to rotate by the motor so that the roller is squeezed by the roller and the fluid in the tube is propelled and moved.
All or a part of the two or more rollers have different projection positions with respect to the rotation axis and around the rotor, and all or a part of the two or more rollers have a non-cylindrical surface around the roller A rotating inner surface is formed on the housing, the rotating inner surface being centered on the rotation axis and facing the peripheral surfaces of the two or more rollers,
Guide means for guiding the tube is formed between the peripheral surface of the two or more rollers and the rotating inner surface, and the rotor is rotated by the peripheral surface of the roller and the rotating inner surface when the rotor rotates. A tube rotary pump characterized by propelling and moving a fluid in a tube. The rotor provided with the guide means and the two or more rollers;
Two or more pairs of the rotating inner surfaces corresponding to the rollers of the rotor are connected with the same rotation axis as the rotation axis,
The tube rotary pump according to claim 1, wherein the guide is provided with the tube. The tube rotary pump according to any one of claims 1 to 3, wherein the guide means is a groove formed around the rotor. The tube rotary pump according to claim 4, wherein the guide means is a protrusion formed to protrude from an inner surface of a groove formed around the rotor.   The tube rotary pump according to claim 2, wherein the roller according to claim 2, wherein the peripheral surface is a non-cylindrical peripheral surface, has a truncated cone shape.

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