JP4675809B2 - Inscribed gear pump rotor and inscribed gear pump - Google Patents

Description

  The present invention relates to an internal gear pump rotor and an internal gear pump for sucking and discharging fluid by changing the volume of a cell formed between tooth surfaces of an inner rotor and an outer rotor.

2. Description of the Related Art Conventionally, a small internal gear type internal gear pump having a simple structure has been widely used as a lubricating oil pump, a fuel pump, etc.
For example, as shown in Patent Document 1 below, such an internal gear pump has an inner rotor formed with n (n is a natural number) external teeth and (n + 1) internal teeth that mesh with the external teeth. An outer rotor formed with a casing and a casing formed with a suction port for sucking fluid and a discharge port for discharging fluid, and rotating the inner rotor in a state in which the outer teeth and the inner teeth are engaged with each other By rotating the outer rotor, the fluid is sucked and discharged by changing the volume of a plurality of cells formed between the rotors.
The cells are individually partitioned by contacting the outer teeth of the inner rotor and the inner teeth of the outer rotor on the front side and the rear side in the rotational direction, and both sides are partitioned by the casing. Each cell has a minimum volume in the process of rotating both rotors, and increases the volume to suck fluid when moving along the suction port. Then, after the volume reaches the maximum, when moving along the discharge port, the volume is decreased and the fluid is discharged.
Japanese Patent No. 3293507

  By the way, in the conventional internal gear pump rotor, when foreign matter is mixed in the fluid, the foreign matter is caught at the meshing position where the inner teeth and the outer teeth mesh to minimize the volume of the cell. There was a risk of stopping the rotation of the pump rotor or damaging the tooth surface.

  The present invention has been made in view of such problems, and an object of the present invention is to provide an inscribed gear pump rotor and an inscribed gear pump that can suppress the biting of foreign matter mixed in a fluid. And

In order to solve the above-described problems, an internal gear pump rotor according to the present invention includes an inner rotor formed with n (n is a natural number) external teeth and (n + 1) internal teeth that mesh with the external teeth. An inscribed type that comprises a formed outer rotor and conveys the fluid by sucking and discharging the fluid by the volume change of the cell formed between the tooth surfaces of the two rotors when the rotors mesh with each other and rotate. The gear pump rotor has a tooth profile of the root of the inner teeth of the outer rotor at the meshing position where the inner teeth and the outer teeth mesh with each other to minimize the volume of the cell. between Sakiitadaki portion, the gap in the radial direction of the internal-type gear pump rotor such that 1.5mm or 3.0mm or less, is about the axis of the outer rotor was an arc shape, the Autaro The said tooth bottom and meshing portions engaged with the outer teeth in the internal teeth of the motor, characterized in that it is connected through a straight portion extending in a radial direction of the outer rotor.
According to the present invention, the tooth profile of the root of the outer tooth of the inner teeth of the outer rotor is such that the tooth of the tooth bottom and the outer tooth is in a meshing position where the inner teeth mesh with the outer teeth and the volume of the cell is minimized. Since the gap in the radial direction of the inscribed gear pump rotor between the top and the top is 1.5 mm or more and 3.0 mm or less, the outer rotor has an arc shape centered on the axial center. A clearance in the radial direction of the inscribed gear pump rotor can be secured between the root of the internal tooth and the top of the external tooth at the meshing position with the rotor having strength enough to withstand actual use. Even if foreign matter is mixed in the fluid, it is possible to suppress the foreign matter from being caught at the meshing position. In addition, since the centrifugal force acts on the foreign matter in the gap without being caught in this way by the rotation of both rotors, the foreign matter is not retained in one place in the inscribed gear pump rotor. It is possible to flow well in the gap, and thereafter, the cell can be discharged to the outside in the process of increasing or decreasing the volume of the cell. Furthermore, in order to achieve the above-described effects, the outer teeth of the inner teeth of the outer rotor are not made smaller than the conventional ones, but the inner teeth of the outer rotor are made smaller than the conventional ones as in the present invention. Since the depth is increased, the liquid-tightness of each cell can be maintained at the same level as the current one, and it is possible to prevent the fluid conveyance efficiency from being lowered.
When the gap is smaller than 1.5 mm, it is not possible to satisfactorily suppress the biting of foreign matter. When the gap is larger than 3.0 mm, it corresponds to the tooth bottom of the inner teeth at the outer peripheral portion of the outer rotor. The thickness of the portion to be reduced becomes too small, and the outer rotor cannot be provided with a strength that can withstand the rotational driving force received from the outer teeth of the inner rotor.

Further, the and the outer teeth and the meshing engagement portion at the inner teeth of the outer rotor and the tooth bottom, since it is connected through a straight portion extending in a radial direction of the outer rotor, before Symbol engagement position, the external teeth In addition to the gap in the radial direction of the inscribed gear pump rotor between the top of the tooth tip and the root of the internal tooth, the tooth tip of this external tooth is excluded from the top of the tooth top, except for the meshing portion that meshes with the internal tooth. It is possible to secure a gap in the circumferential direction of the inscribed gear pump rotor also between the front portion in the rotational direction of both the rotors and the internal teeth. Therefore, it becomes possible not only to more reliably suppress the biting of foreign matter, but also to allow the foreign matter to flow forward in the rotational direction by the centrifugal force, thereby further improving the release of foreign matter. be able to.

Further, in each tooth surface of the external teeth and the internal teeth at the meshing position, there is a gap in the rotational direction between the meshing portions that mesh with each other and the portions facing each other on the rear side in the rotational direction of the inscribed gear pump rotor. It may be 0.05 mm or less.
In this case, since the so-called backlash amount is set to 0.05 mm or less, the above-described effects can be obtained without generating noise.

The inscribed gear pump according to the present invention includes an inscribed gear pump rotor according to the present invention, a suction port through which fluid is sucked and a discharge port through which fluid is discharged while the inscribed gear pump rotor is housed therein. And a drive unit that rotationally drives the inner rotor.
According to the present invention, in the inscribed gear pump rotor, even when foreign matter is mixed in the fluid, it is possible to prevent the foreign matter from being bitten and to be discharged to the outside satisfactorily. As a result, it is possible to reliably prevent the rotational drive of the inscribed gear pump from being stopped or the tooth surface from being damaged due to the presence of foreign matter in the fluid.

  According to this invention, it is possible to suppress biting of foreign matter mixed in the fluid.

Hereinafter, an embodiment of an inscribed gear pump rotor and an inscribed gear pump according to the present invention will be described with reference to FIGS. 1 and 2.
The inscribed gear pump rotor includes an inner rotor 10 in which n (n is a natural number) external teeth 11 are formed, and an outer rotor 20 in which (n + 1) internal teeth 21 that mesh with the external teeth 11 are formed. It is housed inside the casing 30. In the present embodiment, there are 10 external teeth 11 and 11 internal teeth 21.

The inner rotor 10 is connected to a DC motor or a crankshaft of an engine via a rotating shaft (not shown), and is supported so as to be rotatable in the circumferential direction around the axis O1 in the casing 30.
The outer rotor 20 is arranged with its axis O2 eccentric with respect to the axis O1 of the inner rotor 10 (the amount of eccentricity: e) and the inner teeth 21 meshing with the outer teeth 11, and the casing is centered on the axis O2. 30 is rotatably supported in the circumferential direction.

  A plurality of cells C are formed between the tooth surfaces of the inner rotor 10 and the outer rotor 20 along the rotational direction of the rotors 10 and 20. Each cell C is individually partitioned by the contact between the outer teeth 11 of the inner rotor 10 and the inner teeth 21 of the outer rotor 20 on the front side and the rear side in the rotational direction of the rotors 10 and 20, respectively. It is partitioned by the casing 30, thereby constituting an independent fluid transfer chamber. The cell C rotates with the rotation of both the rotors 10 and 20, and repeats the increase and decrease in volume with one rotation as one cycle.

  The casing 30 is formed with an arc-shaped suction port (not shown) along the cell C whose volume is increasing among the cells C formed between the tooth surfaces of the rotors 10 and 20. An arcuate discharge port (not shown) is formed along the cell C in the decreasing process.

  Here, the outer teeth 11 of the inner rotor 10 have, for example, an abduction cycloid curve created by a first abduction circle Ai in which the tooth profile of the tooth tip 11a circumscribes the first basic circle Di and rolls without slipping. And a shape based on an inversion cycloid curve created by a first inversion circle Bi inscribed in the first basic circle Di and rolling without slipping. Has been. Instead of this, the outer teeth 11 of the inner rotor 10 may have a trochoidal tooth profile.

  And in the tooth tip 11a of one external tooth 11, the boundary part of each rotation direction front side among the boundary parts with each tooth bottom 11b respectively connected with the circumferential direction both ends of the inner rotor 10 is the volume of the cell C. At the meshing position K where the tooth tip 11a of the outer tooth 11 and the tooth bottom 21b of the inner tooth 21 are opposed to each other, the inner tooth 21 of the outer rotor 20 is meshed with the rotational driving force of the inner rotor 10. It is made into the meshing part 11k transmitted to.

  The tooth profile of the tip 21a of the inner tooth 21 of the outer rotor 20 is, for example, a shape based on an inversion cycloid curve created by a second inversion circle Bo that is inscribed in the second basic circle Do and rolls without slipping. It is said that. Instead of this, the tooth profile of the tooth tip 21a of the inner tooth 21 of the outer rotor 20 may be a trochoidal tooth profile.

  In the present embodiment, the tooth profile of the tooth bottom 21b of the inner tooth 21 of the outer rotor 20 is between the tooth bottom 21b and the tooth top 11c of the outer tooth 11 of the inner rotor 10 at the meshing position K. The inner gear pump rotor has a circular arc shape centered on the axis O2 of the outer rotor 20 such that a gap t1 in the radial direction is 1.5 mm or more and 3.0 mm or less. The size in the radial direction of the rotor 20 between the tooth bottom 21b and the outer peripheral surface of the outer rotor 20, that is, the wall thickness t2, is set to 1.4 mm or more and 6.0 mm or less.

Furthermore, in the present embodiment, in the inner teeth 21 of the outer rotor 20, the meshing portion 21 k meshing with the meshing portion 11 k of the outer tooth 11 and the tooth bottom 21 b are connected via a linear portion 21 d extending in the radial direction of the outer rotor 20. It is connected. The straight portion 21d extends along a straight line connecting the axis O2 of the outer rotor 20 and the meshing portion 21k. Thereby, at the meshing position K, the clearance between the inner teeth 21 in the circumferential direction gradually increases on the tooth surface of the tooth tip 11a of the external tooth 11 from the meshing portion 11k toward the tooth top portion 11c. It has become.
Further, in the inner teeth 21 of the outer rotor 20, the tooth bottom 21 b and the linear portion 21 d are connected via a concave curved surface portion that is recessed outward in the radial direction of the outer rotor 20.

  Furthermore, in the present embodiment, the tooth profile of the tooth bottom 21b of the inner tooth 21 is bilaterally symmetric with respect to a normal line connecting the axis O2 and the circumferential center of the tooth bottom 21b in a plan view of the outer rotor 20. It is said that the shape. That is, the concave curved surface portion and the linear portion 21d are connected in this order to both ends in the circumferential direction of the outer rotor 20 in the tooth bottom 21b of one internal tooth 21, respectively. Therefore, the portion of the inner tooth 21 excluding the tooth tip 21a, that is, the tooth bottom 21b, the concave curved surface portion and the straight portion 21d respectively connected to both ends in the circumferential direction of the tooth bottom 21b, the plane of the outer rotor 20 is obtained. It is rectangular in shape.

  As described above, at the meshing position K, with the meshing portions 11k and 21k meshing with each other, the entire tooth tips 11a of the outer teeth 11 of the inner rotor 10 and the tooth bottoms 21b of the inner teeth 21 of the outer rotor 20 and the concaves. The curved surface portion and the entire straight portion 21d are not in contact with each other. Further, in each tooth surface of the external teeth 11 and the internal teeth 21 at the meshing position K, the meshing portions 11k and 21k meshing with each other are disposed between the portions 11j and 21j facing each other on the rear side in the rotational direction of the internal gear pump rotor. The clearance in the rotational direction, that is, the backlash amount is 0.05 mm or less.

  As described above, according to the inscribed gear pump rotor and the inscribed gear pump according to the present embodiment, the tooth shape of the tooth bottom 21b of the inner tooth 21 of the outer rotor 20 is the same as that of the inner tooth 21 and the outer tooth 11. At the meshing position K at which the volume of the cell C is minimized, the gap t1 between the tooth bottom 21b and the tooth top 11c of the outer tooth 11 is 1.5 mm or more and 3.0 mm or less. Since the outer rotor 20 has an arc shape centered on the axis O2 of the outer rotor 20, the outer rotor 20 is provided with a strength that can withstand actual use, and the inner tooth 21 has a bottom 21b and an outer surface at the meshing position K. The gap t1 between the teeth 11 and the top 11c of the teeth can be secured, and even if foreign matter is mixed in the fluid, the foreign matter can be prevented from being caught at the meshing position K. .

  In addition, since the centrifugal force acts on the foreign matter in the gap t1 without being caught in this way by the rotation of the rotors 10 and 20, this foreign matter is placed in one place in the inscribed gear pump rotor. It is possible to allow the gap t1 to flow satisfactorily without stopping, and to discharge to the outside in the process of increasing or decreasing the volume of the cell C thereafter. Further, in order to achieve the above-described effects, the tooth length of the outer teeth 11 of the inner rotor 10 is not made smaller than that of the conventional one, but the teeth of the inner teeth 21 of the outer rotor 20 as in this embodiment. Since the bottom 21b is made deeper than before, the liquid tightness of each cell C can be maintained at the same level as the current one, and the fluid conveyance efficiency can be prevented from being lowered.

  Further, since the meshing portion 21k meshing with the external tooth 11 in the inner tooth 21 of the outer rotor 20 and the tooth bottom 21b are connected via a linear portion 21d extending in the radial direction of the outer rotor 20, the meshing position K In this case, not only the gap t1 between the tooth top 11c of the external tooth 11 and the tooth bottom 21b of the internal tooth 21, but also the tooth 11a of the external tooth 11 excluding the meshing portion 11k with the internal tooth 21. It is also possible to secure a gap in the circumferential direction of the inscribed gear pump rotor between the internal teeth 21 and the portion in front of the top portion 11c in the rotational direction of the rotors 10 and 20. Therefore, it becomes possible not only to more reliably suppress the biting of foreign matter, but also to allow the foreign matter to flow forward in the rotational direction by the centrifugal force, thereby further improving the release of foreign matter. be able to.

  Further, in each tooth surface of the external teeth 11 and the internal teeth 21 at the meshing position K, the meshing portions 11k and 21k meshing with each other are disposed between the portions 11j and 21j facing each other on the rear side in the rotational direction of the internal gear pump rotor. Since the gap in the rotational direction is 0.05 mm or less, the above-described effects can be achieved without generating noise.

  In the inscribed gear pump having such an inscribed gear pump rotor, even when foreign matter is mixed in the fluid in both the rotors 10 and 20, the foreign matter is prevented from being caught. In addition, it is possible to discharge it to the outside well, so that foreign matter is mixed in the fluid and the rotation drive of the inscribed gear pump stops or the tooth surface is damaged. It can be surely suppressed.

The technical scope of the present invention is not limited to the above embodiment, and various modifications can be made without departing from the spirit of the present invention.
The type of fluid conveyed by the inscribed gear pump is not limited, for example, fuel such as light oil or lubricating oil.
Furthermore, the number of each of the external teeth 11 and the internal teeth 21 is not limited to that of the above embodiment.

  Moreover, in the said embodiment, as the tooth profile of the tooth bottom 21b of the internal tooth 21, the said concave curved surface part and the linear part 21d are respectively in this order in the circumferential direction both ends of the outer rotor 20 in the tooth bottom 21b of one internal tooth 21. In the plan view of the outer rotor 20, the configuration is shown in which the shape is bilaterally symmetric with respect to the normal line, but the meshing portion 21k of the both end portions of the bottom 21b of one internal tooth 21 is shown. The concave curved surface portion and the straight portion 21d may be connected in this order only to the end portion on the side in the same manner as in the above embodiment.

A verification test was conducted on the effect of the inscribed gear pump described above.
First, schematic configurations of examples and comparative examples according to the present invention will be described.
The outer rotor 20 has an outer diameter of 52 mm, the number of inner teeth 21 is seven, the number of outer teeth 11 of the inner rotor 10 is six, and both rotors 10 have a tooth width of 10 mm. , 20 are housed in the casing 30 to form an inscribed gear pump. In this configuration, the eccentric amount e of both the rotors 10 and 20 is 2.62 mm, and the theoretical discharge amount is 5.3 cm ³ / rev. The discharge pressure was 600 kPa.

In the internal gear pump configured as described above, when the inner rotor 10 is rotated by applying 12V to the DC motor, whether or not the foreign matter is caught and the rotation stops, and the outer rotor 20 is Whether or not breakage such as cracks occurred was verified.
As an embodiment, in the inscribed gear pump shown in FIGS. 1 and 2, two kinds of inscribed gear pump rotors in which the gap t1 is 1.5 mm (Example 1) and 3.0 mm (Example 2), respectively. As a comparative example, two types of inscribed gear pump rotors were prepared in which the gap t1 was 1.2 mm (Comparative Example 1) and 3.2 mm (Comparative Example 2), respectively.

  As a result, in Comparative Example 1, it was confirmed that foreign matter was caught and in Comparative Example 2 that cracks occurred in the tooth bottom 21b of the outer rotor 20, respectively, while in Examples 1 and 2, such foreign matter was found. It was confirmed that no biting or cracking occurred.

  It is possible to suppress biting of foreign matter mixed in the fluid.

It is a section top view of an inscribed type gear pump which has an inscribed type gear pump rotor shown as one embodiment concerning the present invention. FIG. 2 is a partially enlarged view of the inscribed gear pump shown in FIG. 1.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Inner rotor 11 External tooth 11a External tooth tip 11b External tooth bottom 11c External tooth top part 11k External tooth meshing part 20 Outer rotor 21 Internal tooth 21a Internal tooth top 21b Internal tooth bottom 21d Linear portion 21k Internal tooth meshing portion C cell K meshing position O1 Inner rotor shaft center O2 Outer rotor shaft center t1 Clearance

Claims (3)

an inner rotor formed with n (n is a natural number) external teeth and an outer rotor formed with (n + 1) internal teeth meshing with the external teeth,
An internal gear pump rotor that conveys fluid by sucking and discharging fluid by volume change of cells formed between the tooth surfaces of both rotors when the rotors are engaged with each other and rotated,
The tooth profile of the inner teeth of the outer rotor is such that the inner teeth and the outer teeth mesh with each other at a meshing position where the volume of the cell is minimized, between the tooth bottom and the top of the outer teeth. The inner gear pump rotor has a circular arc shape centered on the axis of the outer rotor such that the gap in the radial direction is 1.5 mm or more and 3.0 mm or less ,
An inscribed gear pump rotor characterized in that a meshing portion meshing with the external teeth in the inner teeth of the outer rotor and the tooth bottom are connected via a linear portion extending in a radial direction of the outer rotor. The inscribed gear pump rotor according to claim 1 ,
In each tooth surface of the external teeth and the internal teeth at the meshing position, a gap in the rotational direction between the meshing portions meshing with each other on the rear side in the rotational direction of the inscribed gear pump rotor is 0. An inscribed gear pump rotor, characterized in that the inner gear pump rotor is not more than 05 mm. An inscribed gear pump rotor according to claim 1 or 2 ,
A casing in which the inscribed gear pump rotor is housed and in which a suction port for sucking fluid and a discharge port for discharging fluid are formed,
An internal gear pump comprising: a drive unit that rotationally drives the inner rotor.

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