JP2009162292A5 - - Google Patents

Description

Gear using gear teeth and gear transmission device

  The present invention relates to a gear using an arc tooth profile and a gear transmission device using the gear.

Conventionally, the Wilt Harbor-Nobikov gear (WN gear) is well known as a gear having an arc tooth profile, and research and development related to the arc tooth profile has been promoted in various fields, and a tooth profile combining an arc and another curve. Applied to various gears. The tooth profile is used as a tooth of an internal gear type pump gear, a rack and pinion of an automobile steering device, a gear of a reduction gear, a tooth of a toothed belt, and the like. The present invention is an application related to the previously published Japanese Patent Application Publication No. 2007-32836. The basic idea is based on the invention disclosed above.
Patent Publication 2007-32836 Patent Publication 2002-98219

In the previous patent publication 2007-32836, the feature is described in comparison with a gear having an arc tooth shape that has been conventionally used. However, in the gear according to claim 1 in the patent published claims, the gear does not disclose a gear having a tooth profile that can be offset at an arbitrary interval. . By performing an operation of offset based on the tooth profile curve of the gear according to claim 1 of the published application, the tooth profile can be freely deformed. A tooth profile that allows fine adjustment of the gear size and axial clearance by offsetting the tooth profile curve, as described above, even in the case of a gear having an arc tooth profile so that a shift gear exists in an involute gear. A gear with is required. The gear of claim 1 of the present invention has been devised in view of the foregoing, and provides a gear that satisfies these requirements. Here, terms used in the claims and specification will be explained. Since some technical terms related to gears have different expressions depending on commonly used terms and technical books, they are defined and used as follows in this application text.
External gear A cylindrical gear with teeth arranged on the outside like a spur gear.
External gear In this application, it is used when used as an external gear of an internal gear pump.
Internal gear In this application, it is used when used as an internal gear of an internal gear pump.
Gear transmission device A gear device configured using gears such as a device configured using a pair of gears, a speed reducer, a speed increasing device, and a speed changing device is shown.
Arc radius R In the external gear, the radius (R) of the arc that is the tooth profile of the tooth tip surface.
In the internal gear, the radius (R) of the arc that is the tooth profile shape of the root surface is defined as the arc radius R. It is used as a unit representing the size of the gear teeth of claim 1. (Equivalent to module m in involute gear)
Offset The translation of the base figure at regular intervals.

  In the previous patent publication 2007-32836, the use of a gear having an arc tooth profile is disclosed including examples, but the offset gear is not specifically described including examples. . When various gear devices are configured with a gear having an arc tooth profile, there is a case where it is necessary to adjust the clearance between the shafts of the gear and the gear or it is necessary to adjust the size of the gear. Further, when used as a gear of an internal gear type pump, the suction and discharge capacity may need to be adjusted. When used as a gear of a reduction gear, a gear is required that can give a degree of freedom to the design of the device including the size of the gear, the strength of the teeth, and the size of the casing. Further, there is a need for a gear transmission device that can be composed of a plurality of gears including the gears described above. In view of the foregoing, a gear and gear device that satisfies these requirements is provided.

      In the invention of claim 1, the tooth profile of the tooth tip surface of the external gear is formed by an arc having an arc radius R centered on the reference pitch line, and the tooth profile shape of the tooth bottom surface is the tooth profile of the tooth tip surface adjacent to the reference pitch circle. It is formed by a three-tangent circular arc that circumscribes two circles having a circular arc radius R, and the tooth profile of the external gear is such that the tooth profile arc of the tooth tip surface and the tooth profile arc of the tooth bottom surface are in contact with each other. It is a connected curve, and the tooth profile shape of the tooth bottom surface of the internal gear is formed by an arc having an arc radius R centering on the reference pitch line, and the tooth profile shape of the tooth tip surface is the tooth profile shape of the tooth bottom surface adjacent to the reference pitch circle. The internal gear tooth profile is connected so that the tooth profile arc of the tooth bottom surface and the tooth profile arc of the tooth tip surface are in contact with each other. Based on the center of the reference pitch circle, the tooth profile of the two gears, which is a curved line, is used. A gear having a tooth profile that allows the tooth profile to be offset outward (plus side) or inward (minus side).

A second aspect of the present invention is a gear transmission device including a plurality of gears including the gear according to the first aspect.

The invention of claim 3 is an internal gear pump including a plurality of gears including the gear described in claim 1, and has a structure having functions of a plurality of internal gear pumps in one casing. The multiple internal gear pump has a structure in which the functions of two internal gear pumps are incorporated in one gear pump, and the internal gear (174) has a bias. An intermediate rotor (173) arranged in a center is provided, and the intermediate rotor includes a gear in which a first external gear (176) and a second internal gear (175) are cut on a concentric shaft. And a second external gear (172) arranged eccentrically inside the internal gear (175). The internal gear (174), the external gear (176), the internal gear ( 175) and the external gear (172) mesh with each other and rotate. An internal gear pump that rotates and sucks and discharges fluid between each gear pair. The internal gears (174) and (175) are 1 more than the external gears (176) and (172). This is a multiple internal gear pump in which the number of teeth is large and the tooth tips of both gears slide on the opposite side of the portion where both gears engage with each other most deeply.

A fourth aspect of the present invention is a gear-type pump comprising a plurality of gears including the gear according to the first aspect as an internal gear, and an external gear-type pump and the multiple internal gear-type pump according to the third aspect. This is a combination type gear pump in which the pump is housed in one casing, and its structure is provided with the functions of one external gear pump and four internal gear pumps in one gear pump. A circumscribed inscribed combined gear pump in which the multiple inscribed gear pump described in claim 3 is incorporated in each of the circumscribed gears (201) and (202) of the circumscribed gear pump.

    The gear according to claim 1 is a gear having an arc tooth shape, and the tooth size of the external gear is an arc radius R (hereinafter, defined as an arc radius R) which is a tooth shape of a tooth tip surface. In the gear, it is represented by an arc radius R which is a tooth profile shape of the root surface. The arc radius R can be set to an arbitrary value, and the size of the base gear to be offset is determined by this value and the number of teeth. This arc radius R corresponds to an involute gear module. Compared with the module, there is an advantage that the tooth size is expressed as an actually measured value that can be measured, and the arc radius R can be arbitrarily set depending on the size of the gear device. Further, compared with the involute gear, the meshing is smooth, the vibration is less, and the strength of the tooth portion is increased. Also, there is no tooth-to-tooth interference. The gear train can be formed from a combination of a small number of teeth. Further, the gear according to claim 1 can offset the tooth profile curve outward (plus side) or inward (minus side) based on the center of the pitch circle. The tooth profile curve of the gear can be freely deformed and meshed with each other, and there is a feature that adjustment of the clearance between the shafts and the gear size can be adjusted.

  A gear transmission device according to a second aspect of the present invention is a gear device configured using the gear having the arc tooth profile of the first aspect. It can also be used as a gear of a reduction gear. Compared with a reduction gear used in the past, the design range of the device itself can be reduced from the ease of gear design and the freedom of setting of the arc radius R. It becomes possible to have a degree of freedom, and it is possible to design a device having a large reduction ratio. Furthermore, the use of offset gears leads to a reduction in the weight of the device. Further, the gear of claim 1 can be used for power transmission by the configuration of the internal gear and the external gear, and if the gear train having a small number of teeth is configured, the device itself can be reduced in weight. . When used as an external gear and an internal gear of an internal gear type pump, it becomes possible to freely adjust the discharge amount and the size of the apparatus by the offset amount. Applications can be extended to power transmission devices using deceleration, speed-up, transmissions and other gears.

The internal gear pump according to claim 3 is a multiple internal gear pump configured using the gear having the arc tooth profile of claim 1. Example As shown in FIGS. 16 to 19, it has a function of a plurality of internal gear pumps in one casing, and it becomes possible to store a plurality of pumps in the casing of one pump. This leads to significant labor saving and energy saving.
Further, by adding ancillary facilities such as a pump and piping, a hydraulic circuit, an electromagnetic circuit, etc., it becomes possible to configure the pump as a multi-purpose and multi-specific function. The function of a variable displacement pump can be given as an example.

The inscribed inscribed combined gear pump according to claim 4 is disclosed in the inscribed gear type pump according to claim 3 and Example 4 of Patent Publication 2008-138874 published in the previous application and FIG. This is an application of a circumscribed internal gear pump. One gear-type pump includes one function of the external gear-type pump and four functions of the internal gear-type pump. Compared with the internal gear-type pump according to claim 3, Furthermore, significant labor and energy savings can be expected, and the gear pump is a gear pump that has a large capacity, can be multi-functional and can be used for many purposes.

The gear according to claim 1 of the present invention has a tooth profile curve formed by offsetting the tooth profile curve of the gear according to claim 1 disclosed in the previous patent publication 2007-32836 based on the center of the pitch circle. Gears. Similar to the above-mentioned application, the present invention can be applied to gears having one tooth to an arbitrary number of teeth.
A feature of the gear according to claim 1 of the present invention is that the setting of the arc radius R, which is the size of the tooth, and the offset amount F can be arbitrarily set within a certain range. The offset amount is a distance by which the base graphic is translated at equal intervals. The offset amount is set by the value of the arc radius R representing the size of the gear teeth, and the range that can be offset is the value of the arc radius r of the tangent circle as shown in FIG. 3 and FIG. The upper limit of the outside is the maximum offset amount at the point where the value of r is 0. In other words, it is a point where the arc that touches the 3 contracts and disappears.
On the minus side (inner side), it has been confirmed that the drawing contracts infinitely to the center point o1 of the tooth profile curve on the drawing. However, the range that seems to be effective as a tooth profile curve seems to be up to the point where the value of the arc radius R becomes zero. That is, the arc radius R representing the size of the tooth is 0, and the tooth tip has a pointed shape. Also, when offsetting to the outside relative to the base figure to be offset (here, the tooth profile curve is shown), the offset amount is displayed as a positive value, and when offset to the inside, a negative value is displayed. The offset amount will be displayed. In the previous application, the use of the gear having the offset tooth profile curve has been described in detail, but the gear according to claim 1 of the present invention is also the internal gear of the internal gear type pump. It can be used as a contact gear, and can also be used as an element of an individual gear train of a gear transmission. Further, it has a feature that it can be used as one of the components of the reduction gear disclosed in the previous application.
Here, the tooth profile curve of the gear according to claim 1 of the previous application is compared with the offset tooth profile curve, and its features and effects will be briefly described. Details will be described with reference to the example in the next section.
Features 1) Offset from the arc radius R of the tooth profile curve of claim 1 of the earlier application
Tooth profile curve arc radius R1 (arc radius of offset figure and offset figure
In order to distinguish the arc radius that is the basis of
Is different). In other words, by offsetting the arc radius R
The value and the pitch circle diameter d will increase or decrease. Two arc radius R
The tooth bottom of the external gear and the teeth of the internal gear formed by a three-circular circle that circumscribes the circle
The shape of the tip part is deformed by offsetting, but it is composed of three arcs
What is done is the same. In this case, the arc of the 3-tangent circle shown in FIG. 3 and FIG.
Include a point where the radius r = 0 and a point where the arc radius R1 = 0.
2) The limit that allows offset when offset to the outside is that of the external gear.
In this case, the shape of the tooth bottom of the gear is circumscribed by two adjacent circular arc radius R and pitch circle.
It is formed by a circular arc of 3 tangent circles, but the point where the radius value of this 3 tangent circle is 0
Become a world.
3) The limit that can be offset when inwardly offset is the external gear field.
In this case, the pitch circle shrinks toward the center of the pitch circle, and the value of the pitch circle radius is 0.
Shrink to the point. When offset inward, the value of arc radius R is 0
It seems that the tooth profile curve up to becomes effective in practice. More shrink shape
For practical use because it changes from the shape of the base tooth profile curve to a different shape
Seems to be difficult. Similar results are obtained for the internal gear.
4) It is one of the characteristics of the gear according to claim 1 of the present invention.
Even with a gear whose tooth profile curve is offset based on the center of the pitch circle,
As with the gear set forth in claim 1 of the application, when meshing exactly as a pair of gears,
It has such a great feature.
5) The meshing of the gear teeth is basically the same tooth size in the previous application.
The gear according to claim 1 of the present invention has a tooth profile.
Gears with different tooth sizes (arc radius R) by offsetting the curve
It has the feature that even a person can engage. It is in Example 2 and Example 3
We are explaining in detail.

As an effect, 1) Although the value of the arc radius R representing the size of the tooth changes, the size of the gear can be arbitrarily adjusted.
2) In the meshing of the external gear, it is possible to adjust the axial clearance.
3) The gear tooth size (arc radius R) can be freely set, and the gear design including the gear strength and gear size is facilitated.
4) When a gear transmission device is designed using the gear according to claim 1 of the present invention, it is possible to easily reduce the weight and labor of the device itself.
Hereinafter, embodiments of the present invention will be described with reference to Tables 1 to 11 and FIGS. 1 to 21.

  Table 1 is the same as the table of the internal gear type pump gear basic calculation formula disclosed in Table 1 of the previous application (Patent Publication 2007-32836). When offsetting, it is necessary to obtain basic data of the basic figure (tooth profile curve of the gear). Hereinafter, the offset graphic is referred to as an offset graphic. An offset figure is drawn based on the gear calculation formula in Table 1.

    FIG. 1 is a drawing example of a tooth profile curve based on the external gear (1) in the calculation example of Table 1. A horizontal center line 1u and a vertical center line 1v are drawn. Next, a center line 1w passing through the intersection point o1 at a counterclockwise angle with respect to the vertical center line 1v at the number of teeth division angle α1 is drawn. A pitch circle d11 and a tooth tip circle da11 are drawn around the intersection point o1. Next, a circle 11 and a circle 12 having an arc radius (R) 1 centered on the intersection o11 of the pitch circle d11, the vertical center line 1v and the center line 1w, and the intersection o12 are drawn. A circle 3 that circumscribes the circle 11, circle 12, and pitch circle d11 is drawn. If the arcs 1a and 1b of the drawn circle 11 are connected to the arcs 1b and 1c of the three-tangent circle and the arcs 1c and 1d of the circle 12, a part of the tooth profile curve is drawn. If this tooth profile curve is rotated and copied about the tooth value (5) of the gear centered on o1, the tooth profile curve s1 of the external gear is drawn. Similar to Table 1 above, it is the same as the drawing example disclosed in FIG. 1 of the previous application (Patent Publication 2007-32836). This is a drawing procedure of the external gear necessary for drawing the base figure of the offset figure.

FIG. 2 is a drawing example of a tooth profile curve based on the internal gear (2) in the calculation example of Table 1. A horizontal center line 2u and a vertical center line 2v are drawn. Next, the center line 2w passing through the intersection point o2 is drawn at a counterclockwise angle from the vertical center line 2v at the number-of-teeth division angle α2. A pitch circle d22 and a root circle df22 are drawn around the intersection point o2. Next, an intersection point o21 of the pitch circle d22, the vertical center line 2v, and the center line 2w, and a circle 21 and a circle 22 having an arc radius (R) 1 centering on the intersection point o22 are drawn. A three-tangent circle 23 that circumscribes the circle 21, the circle 22, and the pitch circle d22 is drawn. If the arcs 2a and 2b of the drawn circle 21 and the arcs 2b and 2c of the 3-tangent circle 23 are connected to the arcs 2c and 2d of the circle 22, a part of the tooth profile curve is drawn. If this tooth profile curve is rotated and copied about the tooth value (6) of the gear centering on o2, the tooth profile curve s2 of the internal gear is drawn. Similar to FIG. 1 described above, this is the same as the drawing example disclosed in FIG. 2 of the previous application (Patent Publication 2007-32836). This is a drawing procedure of the internal gear necessary for drawing the base figure of the offset figure.

  FIG. 3 is a drawing of the five-tooth gear of the external gear (1) in the calculation example of Table 1. R represents an arc radius representing the size of the tooth. r is the radius of the arc of a tangent circle where the two circles of the arc radius R constituting the tooth tip part and the pitch circle circumscribe the circle. The offset graphic can be drawn based on the tooth profile curve created by the drawing procedure according to FIGS. Based on o1 which is the center point of the tooth profile curve of FIG. 3, the original tooth profile curve can be deformed with an arbitrary offset amount to the outside (plus side) and inside (minus side). The value of the arc radius R1 of the deformed tooth profile curve and the value of the arc radius r of the tangent circle change in conjunction with the value of the offset amount F. The deformed tooth profile curve is shown in FIG.

FIG. 4 shows a figure offset to the plus side and the minus side based on the tooth profile curve of FIG. The tooth profile curve, which is the reference before offsetting, is highlighted with a bold line. The offset possible range is determined on the plus side by the value of the arc radius r of the tangent circle, and the upper limit of the outside is the maximum offset amount at the point where the value of r is 0. In other words, it is a point where the arc that touches the 3 contracts and disappears. On the plus side, the offset amount F is incremented by 0.2 from 0.2 and the point until the arc radius r of the tangent circle becomes 0 is displayed. The arc radius R of the reference tooth profile curve is 1. On the minus side (inner side), it has been confirmed that the drawing contracts infinitely to the center point o1 of the tooth profile curve on the drawing. However, the range that seems to be effective as a tooth profile curve seems to be up to the point where the value of the arc radius R becomes zero. That is, the arc radius R representing the size of the tooth is 0, and the tooth tip has a pointed shape. Subsequent offset figures continue to shrink toward the center point while maintaining a pointed tip shape. In FIG. 4, the minus side is decreased by −0.2 from the offset amount F = 0, and displays the point where the arc radius R1 = 0 (offset amount F = −1.0). By variously deforming the tooth profile curve of the base to be offset, it is possible to design a wide variety of gear transmission devices using these gears. The tooth profile curve of the base to be offset is disclosed in the previous patent publication 2007-32836. It has a feature that may be offset up tooth profile of any number of teeth from the tooth-shaped curve of small numbers of teeth.

Table 2 lists the basic calculation formulas for the external gear and the internal gear when offset based on the internal calculation formula for the internal gear type pump gear in Table 1. The arc radius representing the size of the tooth is indicated by R, and the offset radius of the offset gear is indicated as R1. Similarly, the offset distance is indicated by the offset amount F, the pitch circle diameter is D, the tip circle diameter is Da, and the root circle diameter is Df.
Some calculation items refer to the data in Table 1. The eccentricity e has a characteristic that it does not change in an internal gear pump using an offset gear. The calculation formulas in Table 2 can be used not only for gears used for internal gear pumps but also for offset gears (external gears and internal gears).

FIG. 5 shows a configuration diagram of the internal gear pump. (A) shows that the external gear has 4 teeth, the internal gear has 5 teeth, and each gear is deformed with an eccentricity e = 0.5 and an offset amount F = 0 drawn with an arc radius R = 1. It is a block diagram of the internal gear type pump which meshes by 1 sheet difference using the tooth profile curve used as the base.
(B) shows the area (hereinafter referred to as the confined area) in which the pump can confine the liquid in the casing by hatching. (C) shows only the confined area, and S0 is the area value. The confinement capacity can be calculated by multiplying the aforementioned area by the tooth width. If CAD software is used, it is possible to easily calculate the area.

  FIG. 6 shows a block diagram of the internal gear pump in which the tooth profile curve of FIG. 5A is offset outward and the confined area value. The offset amount F indicates the combination of the external gear and the internal gear deformed by a value from 0.1 to 0.5. In the case of the internal gear type pump, the offset direction and the offset amount of the external gear and the internal gear must be the same. The eccentricity e has a characteristic that it does not change even if the base tooth profile curve is offset. The offset on the plus side has a feature that the tooth strength can be increased and the discharge capacity can be increased.

  FIG. 7 shows a block diagram of the internal gear pump in which the tooth profile curve of FIG. 5A is offset inward and the confined area value. The offset amount F indicates a combination of an external gear and an internal gear that is deformed with a value from -0.1 to -0.5. Although the discharge capacity is reduced, the apparatus itself can be reduced in weight. It can be seen that the eccentricity e does not change as in FIG. FIG. 6 and FIG. 7 show an embodiment of an internal gear pump constructed by offsetting the basic tooth profile curve. In designing the gear pump, it leads to adjustment of discharge capacity including gear strength and weight reduction of the device. The minus-side offset has a feature that the area for confining the liquid can be increased as the tooth size R becomes smaller, and the discharge capacity can be freely adjusted by design. In addition, the drawing is performed with the arc tooth radius R = 2 of the base tooth profile curve, and the offset amount F = −1.0 (arc radius R = 1) on the minus side and the base tooth profile curve (arc radius R = In the case where the internal gear pump is constructed with these gears after drawing in 1), the internal gear pump constructed by offsetting the gear teeth with the same tooth size has a larger confinement area S. Can be obtained.

  Table 3 shows a case where the value of the arc radius R1, the value of the offset amount F, and the value of the confinement area S of the offset figures in FIGS. 6 and 7 are offset outward and when they are offset inward. Are summarized in a list. It can be seen that the value of the arc radius R1 and the value of the confinement area S increase and decrease in proportion to the value of the offset amount F. That is, it can be seen that the discharge capacity, the respective gear sizes, and the casing size can be proportionally adjusted by the value of the offset amount F. According to the first aspect of the present invention, the tooth profile curve can be freely deformed by offsetting the base tooth profile curve. The gear size, the size of the gear device including the gear, and the tooth profile It is a gear having a feature that the shape can be freely adjusted.

  FIG. 8 is an engagement diagram configured as a rack and pinion (20 teeth) using the gear of claim 1 disclosed in the above-mentioned Japanese Patent Publication No. 2007-32836. This is a figure that is the basis of an offset figure in which the tooth size R = 1 and the offset amount F = 0. The clearance between the rack and the pinion is indicated by a. In the engagement between the rack and the pinion, the distance between the axes is a = d / 2. Here, d represents the pitch circle diameter of the pinion. If the reference pitch of the rack is P, the equation P = π · R is established. R is an arc radius representing the size of a tooth. FIG. 9 and FIG. 10 show the offset figures.

  FIG. 9 is an engagement diagram in which the rack and the pinion of FIG. 8 are offset. The external gear, which is a pinion, is deformed outward (plus direction) with an offset amount F = 0.5, and the rack is increased by the amount of offset of the pinion, so the reverse direction (minus direction) It is the figure which carried out the offset by F = -0.5. In the case of this meshing, the tooth of the pinion side gear becomes thick and the strength of the tooth can be increased. However, the tooth profile on the rack side has a pointed tip and the strength of the teeth is inferior. Which of the rack side and the pinion side is offset to the plus side or the minus side can be freely selected according to the structure of the apparatus and the magnitude of the transmitted power.

    FIG. 10 shows the reverse operation of FIG. That is, an offset amount of 0.5 is given to each of the pinion side in the minus direction (offset amount F = −0.5) and the rack side in the plus direction (offset amount F = 0.5). In this case, it is possible to increase the strength of the teeth on the rack side.

    Table 4 summarizes the external gear data in FIGS. 11, 12, and 13 in a list. FIG. 11 is a drawing based on the basic gear data when the offset amount F = 0, and FIG. 12 and FIG. 13 are the offset drawings based on the data of FIG. The data is shown in Table 4.

FIG. 11 shows an embodiment of a gear train in which an external gear is engaged. FIG. 4 is an engagement diagram of an external gear serving as a base to be offset with an offset amount F = 0.
The inter-axis clearance a can be obtained by the following equation. a = (d3 + d4) / 2 + R. d3 and d4 are pitch circle diameters of the respective external gears, and R represents an arc radius. The arc radius R is the arc radius of the tooth profile curve to be offset, and the arc radius value R in this equation is used as a fixed value that does not change even if the base tooth profile curve is offset in the positive or negative direction. . When the external gears with the offset amount F = 0 are engaged with each other, there is some interference between teeth and tooth advancement and delay during engagement. In order to eliminate this phenomenon, the gear train is constructed by offsetting the basic tooth profile curve as shown in FIGS.

FIG. 12 shows a gear train in which the two external gears of FIG. 11 are combined with the same offset amount F = −0.1. Each gear data is displayed in Table 4 . In the case of a combination of external gears, as described in the above section, when the offset amount is F = 0, tooth interference and tooth advance / delay occur at the time of meshing.
In order to eliminate this phenomenon, the tooth profile curve can be eliminated by combining it with an offset in the positive direction or the negative direction based on the center of the pitch circle. FIG. 12 is taken up as one of the embodiments.

  FIG. 13 shows gear data in Table 4. One external gear is offset by an offset amount F = −0.8 (negative direction), and the other external gear is F = 0.6 (positive). The gear train is combined with an offset in the direction). As described in FIG. 4, the offset possible range is determined by the value of the arc radius r of the tangent circle in the positive direction, and the outer upper limit is the point where the value of r is 0 is the maximum offset amount. Become. In other words, it is a point where the arc that touches the 3 contracts and disappears. For the negative direction, the range that seems to be effective as a tooth profile curve seems to be up to the point where the value of the arc radius R becomes zero. That is, the arc radius R representing the size of the tooth is 0, and the tooth tip has a pointed shape. By setting the above-described offset range for each gear, it is possible to freely select a gear train with an appropriate mesh. Further, the external gear on the left side of the gear train in FIG. 13 is a gear offset in the negative direction. This tooth profile curve can be applied as a roller chain sprocket. For the roller diameter of the chain used for this, it is possible to refer to the arc radius R1 of the external gear in the right diagram of FIG. The gear according to claim 1 of the present invention has a feature that it can be freely deformed by offsetting the tooth profile curve, so that it can be used as an element of a gear device in various directions. It is assumed that.

  Table 5 lists each gear (external gear and internal gear) used in the reduction gears of FIGS. 14 and 15 and basic data of the gear. The tooth size R of each gear before offset is 2, and a gear deformed with an offset amount F = −0.5 is used as a gear of a reduction gear. Each gear data is calculated with reference to the internal gear pump gear basic formula (offset) in Table 2.

  FIGS. 14 and 15 are speed reducers configured with gears offset based on the speed reducers of FIGS. 14 and 15 of the previous application (Patent Publication 2007-32836). FIG. 14A shows a configuration diagram of each gear on the input shaft side. FIG. 14B shows a configuration diagram of the gear on the output shaft side. FIG. 15 shows an assembled cross-sectional view of a speed reducer using offset gears. Table 5 shows the basic data of each gear. The power transmission is transmitted from the input shaft 141 (eccentric shaft of eccentricity e) to the external gear 147 which is the first planetary gear via the bearing 142 (or roller pin) and meshes with the internal gear 148 of the second planetary gear 145. At the same time, the external gear 143 meshes with the fixed sun gear 144 (the internal gear is cut into the input shaft casing cover). The second planetary gear 145 has three gears cut as a unit. The external gear 143 meshes with the internal gear 148 on the input shaft side and the fixed sun gear, and the external gear 151 on the output shaft side. Power is transmitted to the output shaft while the second planetary gear is rocking and meshing with the internal gear 152 that is geared to the output shaft 153. In the case of this speed reducer, the gear ratio between the external gear 147 of the first planetary gear and the internal gear 148 of the second planetary gear meshing with it is not related to the reduction ratio. The gear ratio between the external gear 143 of the second planetary gear and the fixed sun gear 144 and the gear ratio between the external gear 151 on the output shaft side and the internal gear 152 are related to the reduction ratio of the reduction gear. The reduction ratio is explained by the following equation. Reduction ratio i = (zB−zb) / zb × (zb−zd) / zD. zb is the number of teeth of the external gear 143, zB is the number of teeth of the internal gear 144, zd is the number of teeth of the external gear 151, and zD is the number of teeth of the internal gear 152. The reduction gear of the fourth embodiment has a reduction ratio i = 1/1600 from Table 5, and a large reduction ratio can be obtained. In the reduction ratio equation, the difference in the number of teeth of the numerator gear is close to 1, and the larger the number of teeth of the denominator gear, the larger the reduction ratio. When the reduction ratio i is a positive value, the rotation directions of the input shaft and the output shaft are the same. When the value of the reduction ratio i is a negative value, the rotation directions of the input shaft and the output shaft are opposite. Although the reduction ratio has been confirmed to be about 1/3600 in the design and the prototype, it is estimated that a large reduction ratio close to infinity can be obtained by setting the number of gear teeth and the arc radius R. The As described above, the size of the reduction gear and the reduction ratio can be set arbitrarily by setting the arc radius R and the number of gear teeth. Further, by offsetting the gear used for the speed reducer, the gear size and the casing size can be finely adjusted, and the gear tooth strength can be adjusted. Since the mechanism of the internal gear type pump is applied mechanically, it has a feature that it is possible to provide a function for self-supplying the lubrication to the reduction gear. As long as the gear used for the speed reducer can fulfill the configuration and function of the speed reducer, the external gear and the internal gear used for the speed reducer are involute gears, gears having tooth shapes of trochoidal curves, cycloids It is presumed that a gear having a curved tooth profile, or a gear formed by another tooth profile curve can be offset and used as a gear of a reduction gear.

Table 6 is a list of each gear data of the multiple internal gear pump shown in FIG.
The data for each gear is calculated using the basic gear formula in Table 1.
Table 7 is a list of each gear data of the multiple internal gear pump shown in FIG.
The data for each gear is calculated using the gear basic formula (offset) in Table 2.

FIGS. 16 and 17 are configuration diagrams of the gears of the internal gear pump having the functions of two internal gear pumps in one casing. In this configuration, the configuration diagram of the gear reducer shown in FIG. 14A is incorporated in an internal gear pump. The basic data of each gear used in this pump can be easily derived from the gear calculation formulas in Tables 1 and 2 in the same manner as the reduction gear. Compared with a trochoid pump, the basic data of each gear can be calculated with a simple calculation formula. The amount of eccentricity e is 1/2 of the tooth size R, and the amount of eccentricity affects the capacity of the pump. If the gear of claim 1 of the present invention is used, the amount of eccentricity e is An arbitrary pump design with a degree of freedom determined by the tooth size R is possible. Furthermore, by using an offset gear, the pump capacity can be adjusted and the casing size can be adjusted.
Further, by providing the functions of two internal gear pumps in one casing, it is possible to save labor and energy of the apparatus. If the equipment attached to this pump is prepared, a multi-purpose pump configuration including a variable displacement pump is possible.

Table 8 is a list of gear data of the multiple internal gear pump shown in FIG.
The data for each gear is calculated using the basic gear formula in Table 1.
Table 9 is a list of gear data of the multiple internal gear pump shown in FIG.
The data for each gear is calculated using the gear basic formula (offset) in Table 2.

FIG. 18 and FIG. 19 are configuration diagrams of each gear of the internal gear type pump having the functions of three internal gear type pumps in one casing. As in FIGS. 16 and 17, this configuration is obtained by incorporating the configuration diagram of the gear reducer shown in FIG. 14A into an internal gear pump. Multiple configurations of the gears (external gears and internal gears) in the casing can be easily conceived from the configuration diagram of the speed reducer in FIG.
The characteristics of this pump are the same as those described in the description of FIG. 16 and FIG. 17, but it is possible to further promote labor saving and energy saving of the apparatus.
In addition, there is a great possibility that the usage of the pump will be extended to various fields.

  Table 10 shows a basic data table of the external gears 201 and 202 of the external inscribed combined gear pump shown in FIG. The calculation formula of the external gear is calculated based on the calculation formula (1) of Table 1 of the external gear disclosed in JP2008-138874.

  Table 11 shows a basic data table of the external gears 203 and 204 of the externally inscribed combined gear pump shown in FIG. The calculation formula for the external gear is calculated based on the calculation formula (1) for Table 1 external gear disclosed in Japanese Patent Application Laid-Open No. 2008-138874 published in the same manner as Table 10.

FIG. 20 is a circumscribed inscribed combined gear type pump, and shows a diagram in which the circumscribed gear and the inscribed gear are incorporated in the casing body. The multiple internal gear pump units described in the fifth embodiment are fitted inside the external gears 201 and 202, respectively. Each pump has the function of a total of five pumps, one external gear pump section and four internal gear pump sections. If each pump function is used for multiple purposes, or if the suction port and the discharge port are combined into one, it can be used as a pump having a large capacity function. It can be said that it is a labor-saving, energy-saving multipurpose function pump that has the pump function of 5 units in a conventional pump space.

FIG. 21 is a circumscribed inscribed combined gear pump, and shows a diagram in which the circumscribed gear and the inscribed gear are incorporated in the casing body. The multiple internal gear pump units described in the sixth embodiment are fitted inside the external gears 203 and 204, respectively. One pump has one external gear pump section and six internal gear pump sections, and has a function of a total of seven pumps. In addition to the pump shown in Example 7, each pump function can be used for multiple purposes, and if the suction port and the discharge port are combined into one, it can be used as a pump with a large capacity function. It becomes possible to do. It can be said that it is a labor-saving, energy-saving multipurpose function pump that has the pump function of seven units in a conventional pump space. However, in practice, if only one input shaft is used, a great load is generated. Therefore, a gear having the same number of teeth is engaged between the two shafts as two sets of the input shaft 205 and the input shaft 206. At the same time, it becomes possible to operate each of the multiple internal gear pump units.

  A rack cutter, a pinion cutter, a hob cutter, a milling cutter having the gear tooth shape according to claim 1 of the present invention, a generating gear cutting method using a method using any one of the above tools, or the gear according to claim 1 Milling cutters with the following tooth shapes, molding gear cutting method with grinding wheel, and machining program by NC data creation, milling cutter molding method, electrical discharge machine processing method, injection molding machine molding method, casting method, If the gear according to claim 1 is manufactured by any one of the methods, a wide range of production methods can be set from single item production to mass production. Further, as one of the methods for manufacturing the gear according to the first aspect, there is the machining of the NC data from the creation of the gear NC data using the CAD / CAM device to the machining by the NC machine tool. Since the tooth profile curve uses only a plurality of circular arcs, the NC data is mainly composed of circular cutting commands. Accordingly, the NC data capacity is small, and the machining time is shortened.

    The gear according to claim 1 of the present invention can be used widely and widely as an element of a gear transmission device including an external gear of an internal gear type pump, an internal gear, and a gear of a reduction gear. It has the following characteristics.

It is a figure which shows the tooth profile curve of a circumscribed gear tooth number 5 teeth. It is a figure which shows the tooth profile curve of the number of internal gear teeth 6 teeth. It is a figure which shows the tooth profile curve of a circumscribed gear tooth number 5 teeth. It is a figure which shows the tooth profile curve meshing analysis figure of the number of external gear teeth 5 sheets and the number of internal gear teeth 6 sheets. It is a figure which shows the block diagram of the internal gear type pump of 4 external gear teeth number and 5 internal gear teeth number. It is a figure which shows the block diagram of the internal gear type pump with the number of external gear teeth of 4 pieces and the number of internal gear teeth of 5 offset in the positive direction. It is a figure which shows the block diagram of the internal gear type pump with the number of external gear teeth of 4 pieces and the number of internal gear teeth of 5 pieces offset in the negative direction. It is a meshing diagram of rack and pinion (20 teeth) offset amount F = 0. It is a meshing diagram of a rack (offset amount F = −0.5) and 20 pinion teeth (offset amount F = 0.5). It is a meshing diagram of a rack (offset amount F = 0.5) and 20 pinion teeth (offset amount F = −0.5). It is a figure which shows the gear train of offset amount F = 0 with the number of external gear teeth number of 10 and the number of external gear teeth number of 15. It is a figure which shows the gear train of 10 external gear teeth number (offset amount F = -0.1) and 15 external gear teeth number (offset amount F = -0.1). It is a figure which shows the gear train of 10 external gear teeth number (offset amount F = 0.6) and 15 external gear teeth number (offset amount F = -0.8). It is a figure which shows the block diagram of the reduction gear which uses the offset external gear and the internal gear. It is a figure which shows the assembly drawing of the reduction gear which uses the offset external gear and the internal gear. It is a figure which shows the block diagram of the internal gear type pump which uses the gear formula of Table 1. FIG. It is a figure which shows the block diagram of the internal gear type pump which uses the gear formula of Table 2. FIG. It is a figure which shows the block diagram of the internal gear type pump which uses the gear formula of Table 1. FIG. It is a figure which shows the block diagram of the internal gear type pump which uses the gear formula of Table 2. FIG. It is a figure which shows the block diagram of the circumscribed inscribed combination type gear pump using the gear data of Table 10. It is a figure which shows the block diagram of the circumscribed inscribed combination type gear pump using the gear data of Table 11.

11 A circle with an arc radius of 1 centered on o11 in FIG. 1 A circle with an arc radius of 1 centered on o12 in FIG. 1 A 3-circle of circumscribed gear in FIG. 1 2 An arc radius of 1 centered on o21 in FIG. Circle 22 with circle radius 1 centered on o22 in FIG. 2 3-contact circle 141 of internal gear in FIG. 2 Input shaft 142 in FIG. 14 and FIG. 15 Bearing 143 in FIG. 14 and FIG. External gear 144 Internal gear 145 in FIGS. 14 and 15 Second planetary gear 147 in FIGS. 14 and 15 External gear 148 in FIGS. 14 and 15 External gear 148 in FIG. 14, Internal gear 151 in FIG. 15 External gear in FIGS. 152 Internal gear 153 in FIGS. 14 and 15 Output shaft 154 in FIG. 15 Input shaft side casing 155 in FIG. 15 Output shaft side casing in FIG.
161 Input shaft 162 in FIG. 16 External gear in FIG. 16 (small)
163 Intermediate rotor 164 in FIG. 16 Internal gear in FIG. 16 (large)
165 Internal gear (small) in FIG.
166 External gear of Fig. 16 (Large)
171 Input shaft 172 in FIG. 17 External gear in FIG. 17 (small)
173 Intermediate rotor 174 in FIG. 17 Internal gear in FIG. 17 (large)
175 Internal gear (small) in FIG.
176 External gear of Fig. 17 (Large)
181 Input shaft 182 in FIG. 18 External gear (small) in FIG.
183 Intermediate rotor 1 in FIG.
184 Intermediate rotor 2 in FIG.
185 Internal gear of Fig. 18 (large)
186 Internal gear (small) in FIG.
187 External gear of Fig. 18 (middle)
188 Internal gear (middle) in FIG.
189 External gear (large) in FIG.
191 Input shaft 192 in FIG. 19 External gear in FIG. 19 (small)
193 Intermediate rotor 1 in FIG.
194 Intermediate rotor 2 in FIG.
195 Internal gear of Fig. 19 (large)
196 Internal gear (small) in FIG.
197 External gear (middle) of FIG.
198 Internal gear in Fig. 19 (Middle)
199 External gear of Fig. 19 (Large)
201 External gear 202 in FIG. 20 External gear 203 in FIG. 20 External gear 204 in FIG. 21 External gear 205 in FIG. 21 Input shaft 206 in FIG. 21 Input shaft in FIG.
1a Intersection of Figure 1
1b Contact of FIG.
1c Contact point of FIG. 1 1d Intersection point of FIG. 1 2a Intersection point of FIG. 2 2b Contact point of FIG. 2 2c Contact point of FIG. 2 2d Intersection point of FIG. 1 1u Horizontal center line 1v FIG. Dividing angle (α1) index center line
2u Horizontal center line in FIG. 2 2v Vertical center line in FIG.
2w Number of teeth division angle (α2) indexing center line in FIG. 2 a Center distance d1 External gear pitch circle diameter d11 External gear pitch circle d2 Internal gear pitch circle diameter d22 Internal gear pitch circle d3 External gear pitch circle diameter in FIG. d4 external gear pitch circle diameter in FIG. 9 da1 external gear tooth tip diameter da11 external gear tooth tip circle df2 internal gear tooth bottom circle diameter df22 internal gear tooth bottom circle e eccentric amount F offset value o1 external gear center point o2 inside Contact point central point o11 Center point of arc radius in FIG. 1 o12 Center point of arc radius in FIG. 1 o21 Center point of arc radius in FIG. 2 o22 Center point of arc radius in FIG. 2 R Arc radius R1 Arc radius of offset figure r Radius of 3-tangent circle in FIG. 4 S Confinement area α1 of internal gear type pump in FIGS. 5 and 6 Number of teeth division angle of external gear
α2 Internal gear split number of teeth

Claims (4)

      The tooth profile shape of the tooth tip surface of the external gear is formed by an arc having an arc radius R centered on the reference pitch line, and the tooth profile shape of the tooth bottom surface is the tooth profile shape of the tooth tip surface adjacent to the reference pitch circle. Formed by a three-circular arc circumscribing two circles, and the tooth profile of the external gear is a curve connected in such a manner that the tooth profile arc of the tooth tip surface and the tooth profile arc of the tooth bottom surface are in contact with each other; The tooth profile shape of the tooth bottom surface of the internal gear is formed by an arc having an arc radius R centered on the reference pitch line, and the tooth profile shape of the tooth tip surface is 2 of the arc radius R which is the tooth profile shape of the tooth bottom surface adjacent to the reference pitch circle. The tooth shape of the internal gear is a curve that is connected in such a manner that the tooth profile arc of the tooth bottom surface and the tooth profile arc of the tooth tip surface are in contact with each other. Based on the center of the reference pitch circle, the tooth profile of both gears is moved outward ( Gear characterized by having a tooth profile is possible to offset the scan side) or inwardly (negative side). A gear transmission device comprising a plurality of gears including the gear according to claim 1. An internal gear pump including a plurality of gears including the gear according to claim 1 and having a structure having functions of a plurality of internal gear pumps in one casing. The structure is one in which the functions of two internal gear pumps are built in one gear pump, and an intermediate rotor arranged eccentrically inside the first internal gear (174). (173), and the intermediate rotor includes a gear in which a first external gear (176) and a second internal gear (175) are toothed on a concentric shaft, and the internal A second external gear (172) arranged eccentrically inside the gear (175) is provided. The internal gear (174) and the external gear (176), the internal gear (175) and the external gear (172) are provided. ) Each gear meshes with each other and rotates. An internal gear pump that sucks and discharges fluid between a pair, and the internal gears (174) and (175) have one more tooth than the external gears (176) and (172). A multiple internal gear pump in which the tooth tips of both gears slide on the opposite side of the portion where the two gears engage with each other most deeply. A gear pump including a plurality of gears including the gear according to claim 1 as an internal gear, wherein the external gear pump and the multiple internal gear pump according to claim 3 are provided in one casing. The gear type pump is a combination type gear pump having the functions of one external gear pump and four internal gear pumps in one gear pump. 4. A circumscribed inscribed combined gear pump in which the multiple inscribed gear pump described in claim 3 is incorporated in each of the circumscribed gears (201) and (202).