JP2005054709A - Fluid ejector - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a fluid ejector reducing abrasion and improving durability. <P>SOLUTION: A tube 2 where fluid flows in its inside is arranged along the storage wall 34 of the inner wall of the storage section 3A of a case 3. An internal teeth 41 is arranged around the inner periphery of a ring 4 and engaged with an idle gear 6, and the idle gear 6 is engaged with a sun gear 5. When the sun gear 5 is rotated by a motor, the idle gear 6 is revolved while rotating and push-presses the ring 4. The ring 4 eccentrically rotates (rolls) along the storage wall 34, and sequentially transfers and ejects fluid in the tube 2. Rotational movement is transmitted to the ring 4 by the engagement of the gears, therefore, abrasion on the inner periphery of the ring 4 can be reduced, and the durability of a tube pump 1 can be improved. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a fluid ejecting apparatus, and more particularly to a fluid ejecting apparatus that sequentially ejects fluid by pressing fluid flowing through a tube with a ring-shaped pressing member.

  As a fluid discharge device that discharges the fluid flowing inside the tube, the ball disposed on the tube rolls and the tube is sequentially squeezed to discharge the internal fluid, or the ring-shaped member is rotated eccentrically. Various methods have been proposed, such as a method in which a tube is crushed around the outer periphery to discharge a fluid. Among the fluid discharge devices such as these, there is a type in which the ring-shaped member is eccentrically rotated, and the ring-shaped member is driven by an eccentric rotor (for example, Patent Document 1). In this fluid ejection device, the outer periphery of the eccentric rotor is brought into contact with the inner periphery of the ring-shaped member, and the rotation shaft of the eccentric rotor is rotated by a motor or the like. Then, the ring-shaped member rotates eccentrically by the eccentric rotation of the eccentric rotor, rolls on the circularly arranged tubes, and discharges the fluid by sequentially crushing the tubes. In the fluid discharge device having such a configuration, the ring-shaped member is brought into contact with the tube with a relatively large area, so that the rolling friction with respect to the tube is reduced and the burden on the tube can be reduced.

JP 11-62854 A (page 2-3, FIG. 1)

  However, in the fluid discharge device having this configuration, since the ring-shaped member is pressed by the eccentric rotor, friction is generated between the eccentric rotor and the ring-shaped member. For this reason, the inner circumference of the eccentric rotor and the ring-shaped member changes due to use over a long period of time, and the pressing amount of the ring-shaped member against the tube changes, and the tube cannot be pressed properly, and the fluid discharge amount varies. As a result, there is a problem that the fluid discharge device cannot flow out, and the durability of the fluid ejection device cannot be improved.

  An object of the present invention is to provide a fluid ejection device that can reduce wear and improve durability and can secure a stable ejection amount.

  The fluid ejection device of the present invention has a tube in which a fluid flows inside, a circular storage part, a case in which a part of the tube is disposed in contact with the inner wall of the storage part, and a central part of the storage part The sun gear, the idle gear that revolves around the sun gear while rotating in mesh with the sun gear, and the inner teeth that are formed in a ring shape and mesh with the idle gear on the inner peripheral side are formed. And a pressing member that presses the tube on the outer peripheral side by rolling with respect to the inner wall of the storage unit.

  According to the present invention, when the sun gear rotates, the idle gear meshed with the sun gear revolves around the sun gear while rotating. Since the idle gear is meshed with the inner teeth of the pressing member, the pressing member is decentered toward the inner wall of the storage portion while going around the inner periphery of the pressing member. In the pressing member, since the outer peripheral side of the portion with which the idle gear is meshed is close to the inner wall of the storage unit, the tube disposed in contact with the inner wall of the storage unit is pressed. Along with the revolution of the idle gear, the pressing member rotates eccentrically along the inner wall of the storage portion while pressing the tube, so that the fluid in the tube is sequentially pushed out and discharged from the end of the tube.

Since the rotational power of the sun gear is transmitted to the pressing member by meshing the internal gears of the sun gear, the idle gear, and the pressing member, the friction portion between the sun gear, the idle gear, and the pressing member is minimized. The wear of these members is reduced. Accordingly, the torque required for driving the fluid ejection device is reduced, the tube pressing amount does not change even after long-term use, the fluid ejection amount is stabilized, and the durability of the fluid ejection device is improved.
In addition, since the rotational power is transmitted by the meshing of teeth, no slip or the like occurs between the members, power transmission is ensured, and the rotation amount of the pressing member is accurately controlled, so that the fluid discharge amount is accurate. Become. This enables accurate control even when a small amount of discharge is required.
Furthermore, by adjusting the gear ratio of the sun gear, the idle gear, and the internal teeth, the reduction ratio of the pressing member with respect to the rotation of the sun gear can be adjusted, and a wide range of discharge amounts can be handled.

  In the present invention, a disk-shaped reference wheel having a pitch circle size of each tooth is provided on each coaxial axis of the sun gear and the idler gear, and the pressing member is provided with the internal gear coaxially with the central axis of the internal tooth. A ring-shaped internal gear reference wheel having a pitch circle size is provided, and the reference wheel outer periphery of the sun gear and the reference wheel outer periphery of the idle gear are brought into contact with each other, and the reference wheel outer periphery of the idle gear and the internal tooth reference vehicle inner periphery of the pressing member are It is desirable that they are in contact with each other.

According to this invention, the sun gear, the idle gear, and the internal teeth of the pressing member are provided with the reference wheel and the internal tooth reference wheel on the respective teeth. Are respectively in contact with corresponding reference wheels or internal tooth reference wheels. At this time, since the reference wheel and the internal tooth reference wheel are formed in a disk shape or a ring shape of the pitch circle size of each tooth, the teeth of the sun gear, the teeth of the idle gear, and the inner teeth of the pressing member are mutually appropriate. Engage with a good center distance. Therefore, since each tooth does not come closer than the pitch circle of each other, problems such as stopping rotation due to squeaks between teeth are eliminated, and transmission of rotational motion from one to the other is reliable and good. To be done.
Further, since the pressing member receives a reaction force due to the elastic force of the tube, the pressing member may be pressed against the idle gear side by the reaction force, but the internal gear reference wheel of the pressing member, the idle gear reference wheel, and the sun gear Since the radial pressing force is absorbed by contact with the reference wheel, only the tangential force acts on each tooth, the rotation transmission is more reliable and better, and the operation reliability of the fluid ejection device is increased. .

In the present invention, it is desirable to provide a tube fixing means for fixing the tube to the case.
Since there is a difference in diameter between the inner diameter of the storage portion and the outer diameter of the pressing member, when the pressing member makes a round along the inner wall of the storage portion, the pressing member rotates (rotates) by the difference in circumferential length. According to this invention, since the tube is fixed to the case by the tube fixing means, even if the tube is pressed in the circumferential direction of the inner wall of the storage portion by the rotation of the pressing member, the tube moves along the inner wall of the storage portion. Is prevented. Therefore, the relative position of the tube with respect to the case does not change, and the inconvenience that the length from the case to the end of the tube changes due to long-time use is solved.

In the present invention, the case is provided with a tube introduction path that communicates the outside of the case and the storage section. The tube introduction path includes an inflow side introduction path that introduces the tube from the outside of the case to the storage section, and a storage section. It is desirable that a discharge side introduction path for guiding the tube to the outside of the case is provided, and the tube fixing means is provided in the discharge side introduction path.
The pressing member rolls on the tube along the fluid discharge direction. At this time, the pressing member itself rotates in the direction opposite to the fluid discharge direction, that is, toward the fluid inflow side (spinning). Is slightly pressed in this direction. According to the present invention, since the tube fixing means is provided in the discharge side introduction passage, the tube in the case is fixed on the fluid discharge side, and the tube in the case is disposed with a certain amount of tension. It will be. Unlike the case where the tube is fixed on the fluid inflow side and compressive force is applied to the tube in the case, the tube does not move into the case and clogs, and the tube is reliably prevented from moving. Fluid is discharged.

In the present invention, the dimension in the direction along the thickness direction of the pressing member in the gap between the inner wall of the storage portion and the pressing member is preferably smaller than the dimension in the thickness direction of the pressing member.
When the tube is pressed between the pressing member and the inner wall of the storage unit, the tube spreads in the thickness direction of the pressing member. At this time, if the tube spreads outside the end in the thickness direction of the pressing member, the pressing of the tube becomes incomplete, and the fluid may not be sent well.
According to the present invention, the dimension in the direction along the thickness direction of the pressing member in the gap between the inner wall of the storage portion and the pressing member is configured to be smaller than the dimension in the thickness direction of the pressing member. It is surely crushed without escaping on both sides in the thickness direction. Therefore, the fluid in the tube is reliably transferred, a desired discharge amount is obtained, and the fluid discharge amount is stabilized.
Here, the thickness direction of the pressing member refers to a direction along the central axis of the pressing member or a direction along the rotation axis of the sun gear.

In the present invention, the inner wall of the storage portion is formed on both sides of the fluid transfer region, and a fluid transfer region formed so that the dimension between the outer periphery of the pressing member can transfer the fluid by pressing the tube. And a tube introduction region formed so that the dimension between the outer periphery of the pressing member gradually approaches the dimension in the fluid transfer region, and the fluid transfer region is preferably formed at least once.
According to this invention, since the fluid transfer region is formed at least once, the pressing member always presses at least one portion of the tube. Therefore, the back flow of the fluid is prevented, the fluid is continuously and stably transferred, and the discharge amount of the fluid is stabilized. In addition, fluid pulsation is prevented and fluctuations in the discharge amount are suppressed.
Further, since the tube introduction regions are formed on both sides of the fluid transfer region, the tube is introduced into the fluid transfer region while being gradually pressed by the pressing member. Accordingly, since the fluctuation of the fluid volume in the tube is reduced, the occurrence of fluid pulsation is prevented and stable fluid transfer is performed.

In the present invention, it is desirable that a motor for driving the sun gear is connected to the sun gear.
According to this invention, since the sun gear is driven by the motor, the fluid ejection device is automatically driven at a desired constant speed, and the fluid ejection amount is stabilized over a long period of time.

In the present invention, the motor is preferably disposed on the inner peripheral side of the pressing member.
According to the present invention, since the motor is disposed on the inner peripheral side of the ring-shaped pressing member, the space efficiency of the fluid ejection device is improved, and the size reduction of the fluid ejection device is promoted.

In the present invention, it is desirable that a speed reduction mechanism is provided between the output shaft of the motor and the rotation shaft of the sun gear.
According to this invention, since the speed reduction mechanism is provided between the motor and the sun gear, the amount of fluid discharged can be adjusted by adjusting the speed reduction ratio of the speed reduction mechanism. Further, since the rotation of the motor is decelerated and transmitted to the pressing member by the speed reduction mechanism, it is possible to cope with a minute discharge amount, and the application range of the fluid discharge device is widened. Furthermore, high torque can be obtained by decelerating the rotation of the motor by the speed reduction mechanism. For example, even when a highly viscous fluid is discharged, it is possible to sufficiently secure the driving force necessary to press the tube.

In the present invention, the motor includes a rotor, a stator that rotatably holds the rotor, and a coil connected to the stator, and the rotor, the stator, and the coil are arranged on substantially the same plane. It is desirable.
According to the present invention, since the rotor, the stator, and the coil are arranged on substantially the same plane, it is possible to reduce the thickness of the motor, and accordingly, to reduce the thickness of the fluid ejection device.
Here, that the rotor, the stator, and the coil are arranged on substantially the same plane means that at least a part of the rotor, the stator, and the coil are arranged in one plane orthogonal to the rotation axis of the rotor. means.

In the present invention, it is desirable that the rotating shaft of the sun gear and the output shaft of the motor are provided separately and configured to be detachable from each other.
According to this invention, since the rotary shaft of the sun gear and the output shaft of the motor are configured to be detachable, it is possible to appropriately attach the motor selected according to the application, and the versatility of the fluid ejection device is improved. To do. In addition, even if a sun gear or motor side component breaks down, the sun gear rotation shaft and motor output shaft can be removed and replaced with a failed part, reducing the number of replacement parts and reducing maintenance costs. .

In the present invention, it is desirable to provide forcible driving means for forcibly driving the pressing member.
According to this invention, since the pressing member can be forcibly driven by the forcible driving means, the fluid ejection device can be driven with a setting different from the setting during normal driving. For example, when the operation speed of the fluid ejection device is set to be slow, if the drive speed of the forced drive means is set to be high, the forced drive means can transfer the fluid faster than during normal driving. This is useful in that the time required to start use can be shortened because the fluid can be filled faster than normal driving when the fluid is filled into the tube at the start of use of the fluid ejection device.
Also, for example, conversely, if the operation speed of the fluid ejection device is set to be high, if the drive speed of the forced drive means is set to be slow, when the operation of the fluid ejection device is confirmed, it is slowly driven by the forced drive means. This makes it easy to check the setting and operation of the fluid ejection device. As described above, by providing the fluid ejection device with the forcible drive means, it is possible to perform a flexible operation according to various situations.

  Hereinafter, each embodiment of the present invention will be described with reference to the drawings. In the second embodiment and later described below, the same reference numerals are given to the same components and components having the same functions as those in the first embodiment described below, and description thereof will be simplified or omitted.

[First embodiment]
FIG. 1 is a plan view of a tube pump (fluid discharge device) 1 according to the first embodiment of the present invention, and FIG. 2 is a side sectional view of the tube pump 1. 1 and 2, the tube pump 1 includes a tube 2 through which a fluid flows, a case 3 that houses a part of the tube 2, a ring (pressing member) 4 that presses the tube 2, and a ring. 4 includes a sun gear 5 and an idler gear 6 that transmit power to 4, and a drive mechanism 7 that drives the sun gear 5. The ring 4, the sun gear 5, the idle gear 6, and the drive mechanism 7 are housed in the case 3 together with a part of the tube 2.

The case 3 includes a case main body 31 formed in a substantially cylindrical shape, and an upper lid 32 and a lower lid 33 that cover an opening of the case main body 31. The upper lid 32 and the lower lid 33 are fixed to the case main body 31 by screwing or the like.
The case main body 31 has a circular storage portion 3A inside, and the inner wall of the storage portion 3A is a storage wall 34 on which the tube 2 is disposed in contact. The storage wall 34 includes a fluid transfer region 341 in which an internal fluid is transferred when the tube 2 is pressed against the ring 4, and tube introduction regions 342 </ b> A and 342 </ b> B provided on both sides of the fluid transfer region 341. Yes.

FIG. 3 shows a plan view of the case main body 31. In FIG. 3, the storage wall 34 is formed in a spiral shape from the upper lid 32 side toward the lower lid 33 side. The fluid transfer region 341 is formed in one round (360 °) in a circular spiral shape with a diameter R1, and thus has a circular shape in a plan view of the case body 31 (state in FIG. 3).
The tube introduction regions 342A and 342B are formed continuously with the fluid transfer region 341. These tube introduction regions 342A and 342B are formed in a substantially arc shape (spiral shape) whose diameter gradually increases from the diameter R1. The ends of these tube introduction regions 342A and 342B are set such that the difference between the inner periphery of the fluid transfer region 341 and the inner periphery of the tube introduction regions 342A and 342B is larger than the outer diameter of the tube 2. These end portions are connected to tube introduction grooves (tube introduction paths) 343A and 343B communicating from the storage portion 3A to the outside of the case 3. The tube introduction grooves 343A and 343B are formed in a straight line continuously from the arc-shaped partial ends of the tube introduction regions 342A and 342B. The tube introduction regions 342A and 342B and the tube introduction grooves 343A and 343B are continuously formed from the fluid transfer region 341 over about a half circumference (180 °).

The tube 2 is made of an arbitrary material having elasticity such as silicone rubber, for example, and an arbitrary fluid such as a liquid or a gas is circulated therein. The tube 2 passes through one tube introduction groove 343A from the outside of the case main body 31, contacts and is arranged along the inner periphery of the storage wall 34, and is arranged again outside the case main body 31 from the other tube introduction groove 343B. Therefore, one tube introduction groove 343A is an inflow side introduction path through which the fluid in the tube 2 flows from the outside of the case 3 toward the storage portion 3A, and the other tube introduction groove 343B is formed in the tube 2 It is a discharge side introduction path through which the fluid is discharged from the storage portion 3A side toward the outside of the case 3.
FIG. 4 shows the arrangement of the tubes 2 in the case 3. As shown in FIG. 4, the tube 2 is accommodated in the case main body 31 by approximately two turns spirally from the upper lid 32 side toward the lower lid 33 side.

  1 and 2, a stopper (tube fixing means) 21 for fixing the tube 2 to the case 3 is provided at the end of the tube introduction groove 343 </ b> B on the fluid discharge side. The stopper 21 is composed of a cylindrical member whose inner periphery is formed in a circular cross section. The inner periphery of the stopper 21 is fixed to the outer periphery of the tube 2 by adhesion or the like, and the outer periphery is locked to the end of the case body 31. Thereby, the tube 2 is fixed with respect to the case 3, and the movement along the storage wall 34 of the tube 2 is prevented.

The ring 4 is a cylindrical member whose outer diameter is formed with a diameter R2 smaller than the diameter R1 of the fluid transfer region 341 of the storage wall 34, and ring-shaped inner teeth 41 that mesh with the idler gear 6 are provided on the inner periphery. It is fixed. Further, on the inner periphery of the ring 4, a ring-shaped internal tooth reference wheel 42 is formed integrally with the ring 4 on the lower lid 33 side of the inner teeth 41. The inner periphery of the internal tooth reference wheel 42 is formed in a circular shape that matches the pitch circle size of the internal teeth 41.
The outer periphery of the ring 4 is a pressing wall 43 that presses the tube 2, and the dimensions along the axial direction of the sun gear 5 (the thickness direction of the tube pump 1) in the pressing wall 43 are the upper lid 32 and the lower lid 33. , That is, approximately equal to the dimension of the case body 31 in the axial direction (thickness direction, vertical direction in FIG. 2), and is disposed with a predetermined gap between the upper lid 32 and the lower lid 33. ing. The ring 4 is slidably held with respect to the upper lid 32 or the lower lid 33 by contacting the lower lid 33 side end surface of the pressing wall 43 with the lower lid 33 or the upper lid 32 side end surface with the upper lid 32. ing.
Here, the ring 4 is made of an arbitrary low friction coefficient material such as polyacetal so that the frictional force between the upper lid 32 and the lower lid 33 is reduced.

The upper lid 32 and the lower lid 33 are formed with protrusions 321 and 331 that protrude from surfaces facing each other. The protrusions 321 and 331 are formed in a ring shape along the inner periphery of the fluid transfer region 341 (that is, with the outer peripheral diameter R1), and each protrusion dimension D is determined by the distance between the upper lid 32 and the lower lid 33, It is set to be larger than the difference in dimension in the thickness direction of the ring 4. That is, the gaps between the ring 4 and the upper lid 32 and the lower lid 33 are covered by the protrusions 321 and 331.
In the protrusions 321 and 331, the dimension W in the direction parallel to the upper lid 32 and the lower lid 33 is set to be twice or less the wall thickness of the tube 2.

The sun gear 5 is disposed at the circular center of the fluid transfer region 341, and the rotating shaft 51 is pivotally supported by the bearings 322 and 72. The bearing 72 projects from the drive mechanism 7 and also supports the output shaft 71 of the drive mechanism 7. The rotary shaft 51 and the output shaft 71 are connected to each other inside the bearing 72.
Connection portions 511 and 711 that engage with each other are formed at a connection portion between the rotating shaft 51 and the output shaft 71. The connecting portion 511 of the rotating shaft 51 is formed in a concave shape along the axial direction and in a rectangular cross section, and the connecting portion 711 of the output shaft 71 is formed in a convex shape along the axial direction in a rectangular cross section. ing. When the connecting portions 511 and 711 are engaged with each other, the rotating shaft 51 and the output shaft 71 are connected, and the rotation of the output shaft 71 can be transmitted to the rotating shaft 51. Further, the output shaft 71 of the drive mechanism 7 is detachably provided to the rotating shaft 51 of the sun gear 5 by the connecting portions 511 and 711.
A disc-shaped reference wheel 52 formed with a diameter corresponding to the pitch circle size of the sun gear 5 is fixed to the lower cover 33 side of the sun gear 5 on the rotating shaft 51.
A spacer 35 that adjusts the positions of the sun gear 5 and the idle gear 6 in the axial direction is provided between the bearing 72 and the rotary shaft 51, and penetrates the bearing 72. The spacer 35 is fixed to the drive mechanism 7 and adjusts the distance between the upper lid 32 and the drive mechanism 7, that is, the holding position of the rotating shaft 51 of the sun gear 5.

The idle gear 6 is meshed with the inner teeth 41 of the ring 4 and the sun gear 5, respectively, and the rotation shaft 61 is slidably and rotatably held between the spacer 35 and the upper lid 32. A disc-shaped reference wheel 62 having a diameter matching the pitch circle dimension of the idle gear 6 is fixed to the rotary shaft 61 on the lower lid 33 side of the idle gear 6. The outer periphery of the reference wheel 62 is in contact with the outer periphery of the reference wheel 52 of the sun gear 5 and the inner periphery of the internal tooth reference wheel 42 of the ring 4.
Here, the pitch circle size and the number of teeth of the sun gear 5, the idle gear 6, and the internal teeth 41 of the ring 4 are set in advance so that the rotational speed of the sun gear 5 is transmitted to the ring 4 at an appropriate reduction ratio. ing. The dimension obtained by adding the radius of the reference wheel 52 of the sun gear 5, the diameter of the reference wheel 62 of the idle gear 6, and the distance from the inner periphery of the internal reference wheel 42 of the ring 4 to the pressing wall 43 is the storage wall. The half of the diameter R1 of 34 fluid transfer regions 341 (that is, the radius of the fluid transfer region 341) is set to be smaller by twice the thickness of the tube 2. That is, in a state where the sun gear 5, the idle gear 6 and the ring 4 are arranged in a straight line, the distance from the rotating shaft 51 of the sun gear 5 to the pressing wall 43 and half the diameter R1 of the fluid transfer region 341 (fluid transfer) The difference from the distance of the radius of the region 341 is set to be approximately equal to twice the thickness of the tube 2.
The idle gear 6 and the spacer 35 are each preferably made of a material having a low coefficient of friction so that the frictional force can be reduced. In this embodiment, a polytetrafluoroethylene layer is formed on the surface of the idle gear 6. The spacer 35 is formed of polyacetal.

  The drive mechanism 7 is housed in a substantially cylindrical case 73 whose opening end is covered, and an output shaft 71 connected to the sun gear 5 protrudes at a substantially center of the case 73. The case 73 is housed in the case 3 of the tube pump 1, and is on the inner peripheral side of the pressing wall 43 of the ring 4 and on the lower lid 33 side relative to the internal gear reference wheel 42 (the sun gear 5 and the idle gear 6 are provided. It is arranged on the opposite side). At this time, the dimension of the case 73 in the direction parallel to the sun gear 5 and the output shaft 71 (the thickness direction of the tube pump 1, the vertical direction in FIG. 2) is between the internal reference wheel 42 of the ring 4 and the lower lid 33. The drive mechanism 7 is accommodated in the ring 4 also in the direction (the thickness direction of the tube pump 1).

FIG. 5 shows a plan sectional view of the drive mechanism 7. In FIG. 5, the drive mechanism 7 has a configuration in which a motor 74 and a speed reduction mechanism 75 that reduces the rotation of the motor 74 and transmits it to the output shaft 71 are housed in a case 73.
The motor 74 includes a rotor 741 connected to the speed reduction mechanism 75, a stator 742 that rotatably holds the rotor 741, and a coil 743 connected to the stator 742. The rotor 741 is composed of a two-pole permanent magnet, and includes a rotor pinion 741A that meshes with the speed reduction mechanism 75 and an inertia plate (not shown) that reduces uneven rotation of the rotor 741.

The stator 742 includes a plate-like stator portion 742B having a rotor hole 742A that rotatably holds the rotor 741, and a plate-like coil block 742C in which the magnetic core of the coil 743 is integrally formed. The magnetic path can be formed in the rotor 741 and the stator 742 by connecting the 742B and the coil block 742C to form an annular shape. Two notches 742D facing each other are formed on the inner circumference of the rotor hole 742A at positions away from the two pole positions where the rotor 741 is statically stable by a predetermined angle. These notches 742D generate a cogging torque in the rotor 741 so that the rotor 741 stops at a stable position.
The coil 743 is wound around a magnetic core formed in the coil block 742C and has a substantially rectangular cross section.

In the motor 74 having such a configuration, the rotation plane of the rotor 741, the plate-like plane of the stator 742, and the magnetic core of the coil are arranged on the same plane. That is, the motor 74 is a so-called timepiece motor in which the rotor 741, the stator 742, and the coil 743 are arranged on the same plane.
The reduction mechanism 75 includes a gear 751 meshed with the rotor pinion 741A and gears 752 and 753 that are meshed sequentially from the gear 751 and decelerated. The gear 753 meshes with a gear 712 that is fixed to the output shaft 71. The gear ratios of these gears 751, 752, 753, 712 are set in advance so that the reduction ratio from the rotor 741 to the output shaft 71 is appropriate.

In such a tube pump 1, when an alternating current is passed through the coil 743 to rotate the rotor 741 at a predetermined speed, the rotation of the rotor 741 is transmitted while being decelerated by the gears 751, 752, 753, 712 of the speed reduction mechanism 75. The output shaft 71 rotates. The output shaft 71 transmits the rotation to the rotating shaft 51 of the sun gear 5. When the sun gear 5 rotates, the idle gear 6 revolves around the sun gear 5 while rotating. At this time, the rotation direction Q1 (FIG. 1) of the idle gear 6 is opposite to the rotation direction Q2 (FIG. 1) of the sun gear 5, and the revolution direction Q3 (FIG. 1) of the idle gear 6 is This coincides with the rotation direction Q2.
The idle gear 6 presses the ring 4 to the outer peripheral side while revolving, and brings the pressing wall 43 close to the storage wall 34. In this state, since the distance between the fluid transfer region 341 of the storage wall 34 and the pressing wall 43 is almost twice the thickness of the tube 2, the tube 2 is crushed by the pressing wall 43 and the storage wall 34. The internal fluid moves. Since the idle gear 6 revolves along the inner periphery of the ring 4, the ring 4 rotates eccentrically (rolls) along the inner periphery of the storage wall 34, continuously crushes the tube 2, and sequentially transfers the fluid in the tube 2. Transport. Thereby, the fluid is discharged from the end of the tube 2.

When the pressing wall 43 crushes the tube 2, the tube 2 spreads on both sides in the thickness direction of the tube pump 1, but since the dimension in the thickness direction is regulated by the protrusions 321 and 331, the tube 2 has the thickness of the pressing wall 43. It is crushed without entering the gap between the direction end and the upper lid 32 (or the lower lid 33).
In the tube introduction region 342 of the storage wall 34, the distance between the storage wall 34 and the pressing wall 43 gradually increases or decreases. For this reason, in the tube inflow region 342A of the fluid inflow side, that is, the portion introduced from the outside of the case 3 to the fluid transfer region 341 through the tube introduction groove 343A, the amount of pressing by the pressing wall 43 of the tube 2 is the flow of fluid. It gradually increases along the direction. On the discharge side of the tube 2, that is, in the tube introduction region 342B that is guided from the fluid transfer region 341 to the outside of the case 3 through the tube introduction groove 343B, the amount of pressing by the pressing wall 43 of the tube 2 is the flow of fluid. Decrease gradually along the direction.

  Further, since there is a difference in diameter between the outer diameter R2 of the ring 4 (pressing wall 43) and the inner diameter R1 of the fluid transfer region 341 of the storage wall 34, when the ring 4 goes around the inner periphery of the storage wall 34, the ring 4 However, it rotates (spins) toward the fluid inflow side by the difference in the circumference between the outer periphery of the ring 4 and the inner periphery of the storage wall 34. The tube 2 is pressed against the fluid inflow side by the pressing wall 43 by the amount of the deviation, but since the tube 2 is fixed to the case 3 on the fluid discharge side by the stopper 21, the tube 2 in the case 3 is During the operation, it is arranged with a certain amount of tension.

According to such a first embodiment, the following effects can be obtained.
(1) Since the rotational movement of the sun gear 5 is transmitted by the engagement of the idle gear 6 and the inner teeth 41 of the ring 4, unlike the conventional eccentric rotor, the frictional portion between the transmission members can be minimized. Therefore, the wear among the ring 4, the idle gear 6, and the sun gear 5 can be reduced, and the distance between the pressing wall 43 and the storage wall 34 can be appropriately maintained even after long-term use. Therefore, the tube 2 can be pressed well and a stable fluid discharge amount can be secured.
Further, since the rotational motion is transmitted by the meshing of the gears, no slip occurs between the transmission members, and the tube pump 1 can be driven with a relatively small torque and the rotational motion can be transmitted well. Therefore, the transmission efficiency from the sun gear 5 to the ring 4 can be improved. And since rotation movement can be reliably transmitted by meshing | engagement of a gearwheel, a fluid can be discharged correctly.

 (2) The sun gear 5, the idler gear 6 and the ring 4 are provided with reference wheels 52, 62 and an internal tooth reference wheel 42, respectively. Since the reference wheel 52, 62 and the internal gear reference wheel 42 are brought into contact with each other, the center distances of the sun gear 5, the idle gear 6, and the ring 4 are appropriately adjusted. Can hold. Therefore, an appropriate backlash can be ensured between the respective teeth and the teeth can be meshed well with each other, so that the transmission efficiency of the rotational motion can be improved.

  Further, when the tube 2 is pressed by the pressing wall 43, the ring 4 is pressed inward by the reaction force due to the elastic force of the tube 2. At this time, since the sun gear 5, the idle gear 6, and the ring 4 are in contact with the reference wheels 52 and 62 and the internal tooth reference wheel 42, it is possible to prevent the teeth from approaching each other beyond the pitch circle dimension. . Therefore, it is possible to prevent the sun gear 5, the idle gear 6, and the inner teeth 41 of the ring 4 from being strongly engaged with each other and being fixed, and the rotation stop of the ring 4 can be reliably prevented. Thereby, even when using the tube 2 with a large restoring force (elastic force), for example, the fixation of teeth can be reliably prevented and the rotational motion can be transmitted well. Since the reference wheels 52 and 62 and the internal gear reference wheel 42 absorb the radial reaction force of the sun gear 5 due to the elastic force of the tube 2, the sun gear 5, the idle gear 6, and the internal teeth 41 of the ring 4. In this case, only a tangential force is applied, and the rotational motion of the sun gear 5 can be transmitted with high efficiency.

  Further, since the center distances of the sun gear 5, the idle gear 6, and the ring 4 can be appropriately maintained by the reference wheels 52 and 62 and the internal tooth reference wheel 42, the rotation shaft 61 of the idle gear 6 is, for example, the upper lid 32 and There is no need to regulate the position of the rotating shaft by supporting it with the spacer 35, and the structure can be simplified. In addition, since the idle gear 6 is not pivotally supported, positioning when the tube pump 1 is assembled can be easily performed, so that the assembling property of the tube pump 1 can be improved. And since there is no need to support the idle gear 6, the resistance applied to the bearing can be removed, and the rotational motion can be transmitted with higher efficiency.

(3) Since the tube introduction regions 342A and 342B are formed in the storage wall 34, the tube 2 can be gradually introduced into the fluid transfer region 341, and can be gradually guided from the fluid transfer region 341 to the outside of the region. it can. That is, since the amount of pressing by the pressing wall 43 of the tube 2 can be gradually increased or decreased, the volume change of the fluid in the tube 2 can be suppressed to the minimum. Therefore, the occurrence of pulsation of the fluid in the tube 2 can be prevented, and the fluid discharge amount can be stabilized.
In addition, since the fluid transfer region 341 is provided for one round (360 °), the ring 4 can always press one portion of the tube 2 completely and transfer the fluid. Thereby, the back flow of the fluid in the tube 2 can be prevented, and the occurrence of pulsation can also be prevented by this, so that more stable fluid transfer can be performed.

(4) Since the rotation of the motor 74 is decelerated by the decelerating mechanism 75, high torque can be obtained at the output shaft 71. Therefore, for example, even when it is desired to discharge a highly viscous fluid, it can be satisfactorily handled. Further, the deceleration mechanism 75 can accurately cope with a minute discharge amount.
Further, the motor 74 is a stepping motor having a rotor 741, a stator 742, and a coil 743. By reducing the rotation of the rotor 741, the fluctuation range of the rotational speed of the rotor 741 can be reduced, and the ring 4 Can be driven smoothly. Thereby, the discharge amount of the fluid can be stabilized and pulsation can be prevented.
In addition to the reduction by the reduction mechanism 75, the rotational speed from the motor 74 can be reduced to some extent by adjusting the gear ratio of the sun gear 5, the idle gear 6, and the internal teeth 41 of the ring 4. Therefore, the present invention can be effectively applied to a case where the discharge amount is smaller, a case where deceleration is difficult only by controlling the motor 74, or a case where more driving torque is required. Since the sun gear 5, the idle gear 6, and the internal teeth 41 of the ring 4 can reduce the speed to some extent, the reduction ratio of the speed reduction mechanism 75 can be reduced. Therefore, the number of gears of the speed reduction mechanism 75 can be reduced, and the structure of the speed reduction mechanism 75 can be simplified. Thereby, size reduction of the tube pump 1 can be promoted.

 (5) Since the sun gear 5 is driven by the motor 74, the ring 4 can be driven at a predetermined constant speed, and the amount of fluid discharged can be stabilized. Further, since the motor 74 is a so-called watch motor in which the rotor 741, the stator 742, and the coil 743 are arranged on the same plane, the motor 74 can be made thinner, and therefore the tube pump 1 can be made thinner. Can promote. Further, by changing the shape of the stator 742, the rotor 741 and the coil 743 can be freely arranged on a plane, so that the degree of freedom of arrangement can be increased and the downsizing of the tube pump 1 can be promoted. On the contrary, since the rotor 741, the stator 742, and the coil 743 can be arranged with high space efficiency in the same space, high efficiency and low power consumption of the tube pump 1 can be realized. Thereby, it can apply also as a portable tube pump 1, for example.

(6) Since the stopper 21 is provided, the tube 2 can be fixed to the case 3. That is, the ring 4 rotates on the inner periphery of the storage wall 34 to rotate in the direction opposite to the fluid transfer direction, so that the tube 2 is pressed toward the fluid inflow side. It can prevent moving along 34, and can prevent that the length of the tube 2 before and behind the tube pump 1 changes. Therefore, the tube pump 1 can be used for a long time without adjusting the length of the tube 2.
Further, since the stopper 21 is provided in the tube introduction groove 343B on the fluid discharge side, the tube 2 inside the case 3 is disposed with a certain amount of tension by the rotation of the ring 4. Therefore, the tube 2 can be prevented from entering the inside of the case 3 as compared with the case where a compressive force is applied to the tube 2, and problems such as the rotation stop of the ring 4 due to the slack of the tube 2 can be reliably prevented.

 (7) Since the projections 321 and 331 are provided on the upper lid 32 and the lower lid 33, the end portion of the pressing wall 43 in the direction (thickness direction) parallel to the axial direction of the sun gear 5, the upper lid 32 and the lower lid 33. The gap between can be closed. Therefore, since the tube 2 is disposed between the pressing wall 43 and the storage wall 34 without escaping to the gaps on both sides in the thickness direction of the pressing wall 43, the tube 2 can be crushed reliably and satisfactorily by the pressing wall 43. Therefore, fluid transfer mistakes and the like can be prevented, and the fluid discharge amount can be stabilized.

(8) The drive mechanism 7 is a unit housed in the case 73, and this unit is also on the inner peripheral side of the ring 4 and in the direction parallel to the axial direction of the sun gear 5 (the thickness direction of the tube pump 1). Since it is arranged inside the ring 4, the entire drive mechanism 7 can be stored inside the ring 4. Therefore, the tube pump 1 can be reduced in thickness and size.
Further, since the output shaft 71 and the rotating shaft 51 of the sun gear 5 are configured separately and the connecting portions 511 and 711 are formed at the opposing ends, respectively, the entire drive mechanism 7 can be easily formed as one unit. It can be removed from the sun gear 5. Since the drive mechanism 7 can be attached to and detached from the sun gear 5 in this way, the tube pump 1 with different drive settings can be manufactured by incorporating the drive mechanism 7 with different reduction ratios into the common tube pump 1. The pump 1 can be flexibly adapted to various drive settings while sharing the parts of the pump 1. For example, even when the tube pump 1 is used for feeding medical chemicals, if each tube pump is prepared for each chemical and only the drive mechanism 7 is replaced, each chemical can be fed without sanitary problems. In addition, the drive mechanism 7 can be shared.
In addition, when the drive mechanism 7 or the sun gear 5 or the idle gear 6 needs to be replaced, the drive mechanism 7 and the sun gear 5 are detachable. Replace it. Therefore, the number of replacement parts can be reduced, and the maintenance cost of the entire tube pump 1 can be reduced.

[Second Embodiment]
Next, a second embodiment of the present invention will be described. In the second embodiment, a forced drive means is provided in the tube pump 1 of the first embodiment.
The top view of the tube pump 1 concerning 2nd embodiment is shown by FIG. In FIG. 6, the tube pump 1 includes forcible drive means 8 for forcibly driving the ring 4.
The forcible drive means 8 includes a handle 81 connected to the rotating shaft 51 of the sun gear 5 and a clutch mechanism 82 provided so that power transmission from the rotating shaft 51 of the sun gear 5 to the motor 74 can be cut off. Has been. The handle 81 is disposed outside the case 3 and is fixed to the rotating shaft 51 of the sun gear 5 that penetrates the upper lid 32 and protrudes outside the case 3.

The clutch mechanism 82 includes a disc spring 821 provided on a gear 712 of the output shaft 71, and the disc spring 821 has a gear-like 712 and a disc-shaped friction member 822 formed integrally with the output shaft 71. Pressing with spring force. With this pressing force, the gear 712 and the friction member 822 are connected by a frictional force. The clutch mechanism 82 by the disc spring 821 is not limited to the gear 712 and may be provided in any of the gears (gears 751, 752, 753) of the speed reduction mechanism 75.
In such a tube pump 1, when the handle 81 is turned, the sun gear 5 is directly driven to rotate and fluid is discharged. At this time, when the rotation speed of the handle 81 becomes equal to or higher than a predetermined value and a torque equal to or higher than a predetermined value is applied to the gear 712, the gear 712 and the friction member 822 resist the frictional force caused by the pressing force of the disc spring 821. Sliding and rotating motion is not transmitted to the gear 712.

According to the second embodiment, in addition to the same effects as the effects (1) to (8) of the first embodiment, the following effects can be obtained.
(9) Since the forced drive means 8 is provided in the tube pump 1, the tube pump 1 can be driven with different settings separately from the normal drive by the drive mechanism 7. That is, for example, when the reduction ratio of the speed reduction mechanism 75 is set to be large, it takes a long time to fill the tube 2 with fluid when starting to use the tube pump 1. In such a case, if the sun gear 5 is directly driven by driving the handle 81, the fluid in the tube 2 can be transferred quickly and the time required for preparation for use can be shortened. Moreover, when the use of the tube pump 1 is terminated, the time for discharging the fluid in the tube 2 can be shortened.
In this way, the tube pump 1 can be driven with different settings by the forcible drive means 8, so that a wide discharge amount range can be accommodated. This is useful, for example, when the discharge amount must be changed according to circumstances.
Further, since the handle 81 can be operated manually, it can be used as an emergency drive means when the power source such as a battery is exhausted.

 (10) Further, since the clutch mechanism 82 by the disc spring 821 is provided, when a torque of a predetermined value or more is applied by driving the handle 81, it is possible to prevent the rotational motion from being transmitted any further. Therefore, damage to the motor 74 and the speed reduction mechanism 75 can be reliably prevented.

The present invention is not limited to the above-described embodiments, and modifications, improvements, and the like within the scope that can achieve the object of the present invention are included in the present invention.
The tube is not limited to the one that is spirally arranged along the inner wall of the housing portion of the case, but may be arranged to be abutted about once in the case 3 as shown in FIG. 7, for example. . Even in this case, since the ring 4 always presses one portion of the tube 2 completely, the fluid can be transferred well. In short, the tube only needs to be arranged so that it is completely pressed against the pressing member at least at one place.
Further, at this time, the tube introduction region does not necessarily have to be formed about half a circle (180 °). You may set suitably. Further, for example, as shown in FIG. 7, the tube introduction region may not be formed and may be directly connected to the tube introduction grooves 343 </ b> A and 343 </ b> B from the fluid transfer region 341.

The sun gear, idle gear, and inner teeth of the ring can increase / decrease to some extent. If the desired driving speed, driving torque, etc. can be obtained by increasing / decreasing within this range, the motor (driving means) is directly connected. do it. Therefore, the speed reduction mechanism is not necessarily provided. When the speed reduction mechanism is not provided, the drive mechanism becomes simple and the fluid discharge device can be further reduced in size.
The motor is not limited to one in which the rotor, the stator, and the coil are arranged on the same plane, but at least a part of each other overlaps each other when viewed from the side of the motor, that is, when the motor is viewed from the plane direction of the stator. Furthermore, it is sufficient that they are arranged on substantially the same plane.
The motor is not limited to a stepping motor having a rotor, a stator, and a coil, and any other motor can be employed.

In the second embodiment, the forcible drive means is set so that it can be driven faster than the drive speed of the drive mechanism 7, but is not limited to this, and is set to drive slower than the drive setting speed of the drive mechanism, for example. Also good.
Further, in the second embodiment, the forcible drive means is to manually operate the handle 81 to drive the sun gear 5, but not limited thereto, for example, a motor is connected to the rotation shaft of the sun gear, The sun gear may be driven automatically.
Further, the forcible drive means is not limited to the one that rotationally drives the sun gear, and may be one that is connected to, for example, an idle gear or a pressing member and rotationally drives them by some method.
The sun gear, the idle gear, and the pressing member are not necessarily provided with the reference wheel and the internal gear reference wheel, respectively. Even in such a case, when the reaction force due to the elasticity of the tube is small, the sun gear, the idle gear, and the internal teeth can be satisfactorily engaged, so that the fluid discharge device can be driven.

The best configuration, method and the like for carrying out the present invention have been disclosed in the above description, but the present invention is not limited to this. That is, the invention has been illustrated and described primarily with respect to particular embodiments, but may be configured for the above-described embodiments without departing from the scope and spirit of the invention. Various modifications can be made by those skilled in the art in terms of materials, quantity, and other detailed configurations.
Therefore, the description limited to the shape, material, etc. disclosed above is an example for easy understanding of the present invention, and does not limit the present invention. The description by the name of the member which remove | excluded the limitation of one part or all of such restrictions is included in this invention.

  Such a fluid discharge device is suitable for, for example, a tube pump for medical drug administration because the fluid flows in the tube and the mechanism for discharging the fluid is arranged outside the tube and does not directly contact the fluid. is there. Further, since the fluid ejection device of the present invention can be reduced in size, it can be applied to a portable fluid ejection device. Furthermore, the liquid ejection device of the present invention is capable of micro-ejection, has excellent portability, and has low power consumption. Therefore, for example, a portable pump for medical use and beverage for administration of insulin, cancer pain medicine, etc. Injection, mixing food pumps, pumps for supplying fuel for fuel cells, cooling pumps for circulating cooling water around CPUs and power supplies for small devices, injection of reagent, mixing, etc. It can be used for analysis pumps.

The top view which shows the fluid discharge apparatus concerning 1st embodiment of this invention. 1 is a side sectional view showing a fluid ejection device according to a first embodiment. The top view which shows the storage wall concerning 1st embodiment. The perspective view which shows arrangement | positioning of the tube concerning 1st embodiment. The top view which shows the drive mechanism concerning 1st embodiment. The top view which shows the fluid discharge apparatus concerning 2nd embodiment of this invention. The figure which shows the modification of a fluid discharge apparatus.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Tube pump (fluid discharge apparatus), 2 ... Tube, 3 ... Case, 3A ... Storage part, 4 ... Ring (pressing member), 5 ... Sun gear, 6 ... Play gear, 7 ... Drive mechanism, 8 ... Force drive Means, 21 ... Stopper (tube fixing means), 34 ... Storage wall, 41 ... Internal tooth, 42 ... Internal tooth reference wheel, 52, 62 ... Reference wheel, 43 ... Press wall, 71 ... Output shaft, 74 ... Motor, 75 ... deceleration mechanism, 321, 331 ... projection, 341 ... fluid transfer area, 342A, 342B ... tube introduction area, 343A, 343B ... tube introduction groove (tube introduction path), 741 ... rotor, 742 ... stator, 743 ... coil.

Claims (12)

A tube in which a fluid flows, a case having a circular storage portion, a part of the tube being disposed in contact with the inner wall of the storage portion, and a sun gear disposed in the center of the storage portion; An idle gear that revolves around the sun gear while rotating in mesh with the sun gear, and an inner tooth that is formed in a ring shape and meshes with the idle gear on the inner peripheral side, and A fluid ejection device comprising: a pressing member that presses the tube on the outer peripheral side by rolling with respect to the inner wall of the storage unit. 2. The fluid ejection device according to claim 1, wherein a disk-shaped reference wheel having a pitch circular dimension of each tooth is provided on each of the coaxial axes of the sun gear and the idle gear, and the pressing member A ring-shaped internal gear reference wheel is provided coaxially with the central axis of the tooth and with a pitch circle size of the internal teeth, the reference wheel outer periphery of the sun gear and the reference wheel outer periphery of the idle gear are in contact with each other; The fluid discharge device according to claim 1, wherein the reference wheel outer periphery of the idle gear and the inner reference wheel inner periphery of the pressing member are in contact with each other. The fluid ejection device according to claim 1 or 2, further comprising a tube fixing means for fixing the tube to the case. 4. The fluid ejection device according to claim 3, wherein the case is provided with a tube introduction path that communicates the outside of the case and the storage portion, and the tube introduction path extends from the outside of the case to the storage portion. An inflow side introduction path for introducing the tube, and a discharge side introduction path for guiding the tube from the housing portion to the outside of the case, wherein the tube fixing means is provided in the discharge side introduction path. Fluid discharge device. 5. The fluid ejection device according to claim 1, wherein a dimension of the gap between the inner wall of the storage portion and the pressing member along a thickness direction of the pressing member is a thickness direction of the pressing member. A fluid discharge device characterized by being configured to be smaller than the dimension of 6. The fluid ejection device according to claim 1, wherein the inner wall of the storage portion is formed such that a dimension between the inner wall and the outer periphery of the pressing member can transport the fluid by pressing the tube. And a tube introduction area formed on both sides of the fluid transfer area and formed so that the dimension between the outer periphery of the pressing member gradually approaches the dimension in the fluid transfer area. And the fluid transfer region is formed at least once. The fluid ejection device according to any one of claims 1 to 6, wherein a motor that drives the sun gear is connected to the sun gear. 8. The fluid ejection device according to claim 7, wherein the motor is disposed on an inner peripheral side of the pressing member. 9. The fluid ejection device according to claim 7, wherein a speed reduction mechanism is provided between an output shaft of the motor and a rotation shaft of the sun gear. 10. The fluid ejection device according to claim 7, wherein the motor includes a rotor, a stator that rotatably holds the rotor, and a coil connected to the stator. The stator and the coil are arranged on substantially the same plane. 11. The fluid ejection device according to claim 7, wherein the rotating shaft of the sun gear and the output shaft of the motor are provided separately and configured to be detachable from each other. A fluid discharge device. The fluid ejection device according to claim 1, further comprising a forcible driving unit that forcibly drives the pressing member.

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