KR870001604B1 - Method of transforming rotating movement to sliding movement using internal gear - Google Patents

Abstract

An intermittent internal gear with a portion of its teeth removed is engaged with two or more in even number of spur gears, which in turn reciprocate an oscilatory movement. In modification, the two pinion spur gears may have intermediate link gears in an even number between them to simultaneously bring a number of oscilatory movements.

Description

Mechanism for converting rotational motion into oscillatory motion by using tooth decay gear

1 is a plan view in which spur gears of one phase are inscribed and interlocked in one internal tooth gear.

2 is a plan view in which two spur gears of different sizes are inscribed and engaged with each other in a single toothless gear.

3 is a simplified illustration of several spur gears in a single tooth gear.

4 is interlocked with four identical spur gears inscribed in one toothless gear.

In the present invention, an input rotary gear is formed by removing some teeth of an internal gear, and placing two or even ordinary spur gears which are internally inscribed and bite each other. As the output swing gear, two gears (or more excellent gears) inscribed therein are sequentially transmitted by the rotation of the internal toothing gear, and the rotational force is transmitted to the other gear so that the gear teeth This mechanism is designed to generate the opposite rotational force, that is, the oscillation force whenever the bite of the gear changes from one spur gear to the other spur gear. It is a kind of mechanism that converts it into oscillation.

Up to now, many cranks and links have been used to convert rotational movements into oscillatory motions. The bearings cannot be supported on both sides of the rotational axis, and the swing angle is limited, so the center of rotation The angle was large around 90 °, the reciprocating swing time was not the same (sometimes it was used as an advantage), and there were many problems such as a lot of driving force at the chang point. This invention solves these defects, and at the same time, it is easy to obtain a large opposite rotation angle of about 180 ° -360 ° in two or more axes.

The embodiments will be described below with reference to the accompanying drawings.

Example 1

Figure 1 shows a pair of common spur gears B and B 'inscribed on a single anchoring gear A and fixed to axes S _b and S _b' respectively, interlocking with each other, and C _a on one side of the internal gear. Cams are attached and C _b and C _{b '} are corresponding cams attached to gears B and B', respectively, and are arranged to act as a zeneva stop according to the rotation of the gear A in R direction. Fixed. When A gear meshes with B gear and rotates in R direction, B 'gear turns to L direction as opposed to B. When A gear is engaged with B gear and A gear meshes with B' gear and turns to R direction, B gear goes to L direction. Turn to That is, the B gear and the B 'gear have a certain swing angle and swing in opposite directions.

Here, the size of the center angle of the part where the endend circle of the internal gear and the internal end of the inscribed spur gear interfere with each other, that is, the size between the points P _e and P _s '(or P _s and P _e ') Alternatively, it is expressed as β by the number of pitches. If the total number of teeth that can be produced in internal gear A is Z _a , the number of teeth of spur gears B and B 'is Z _b , and the maximum number of teeth that can be left in internal gear A is αx, the size of β

This can be found in general, where Z _a = 2Z _b , as in the first diagram, that is, if the gears B and B 'are the same size,

It becomes

Where α _x is

Is an integer within the range satisfying, and if the number of teeth that can be left on the internal gear is generally α,

α _x ≥α≥1

to be.

In Figure 1 Z _a = 24, Z _b = 12 and β _x 4.31, so α _x = 8. In other words, you can leave α = 1 to 8 teeth in the internal gear A. Here, α = 8 is engaged with the teeth of the A gear, so that it rotates in the R direction. The point where the gear B stops without turning further by P _{e is the} point where the gear A stops further in the R direction and acts as a Geneva stop until A's first tooth engages the teeth of B 'gear. C _a and C _b mesh together to stop B and B 'gears in place.

However, in the case of FIG. 1, when S is the so-called starting point at which the first contact action occurs at the first end of the A gear and the second end of the B 'gear, S is the interference range point P _s of the two gears. 1 of gear A is caught by gear B 'and cannot transmit torque properly. Therefore, at this time, lower the number 2 teeth of B and B 'gears or the number 1 teeth of A gears, that is, the lower teeth, and the first gear of A gear is sufficiently engaged with the first teeth of B and B' gear. It is good to let the action begin. Alternatively, tooth 8 of gear A or tooth 8 of gears B and B 'should be lowered so that 1 of A is sufficiently bited into 2 of B' and B.

As A gear turns B gear to R direction and B gear stops, distance of center line connecting B and B's gear axis S _b and S _b 'to the center line of tooth B's 10 teeth If is expressed as the center angle, and ε, the angle of ε also exists with the end of No. 12 in the B 'gear. (Ignore the gear's backlash for convenience.)

인데 정수부를 제외한 소수부분의 크기 0.155=k라 하면

로 표시되며, k가 0＜k＜0.5일 때 B기어의 ε은 기어 이빨이 아닌 홈(space)에 놓이게 되며, 0.5＜k＜1의 범위에 있을 때에는 ε은 이빨 두께위에 놓이게 된다. 또 k가 0.5보다 작은 경우에 k=ε으로 보고, k가 0.5보다 클 때에는 k-0.5=ε으로 하면 제 1 도에서 B기어가 정기된 순간 B기어위의 ε은 ε=0.155가 되어 ε이 홈 위에 오며, Z_b=Z_b'이면서 우수이므로, B'기어에서는 이빨외 이 두께위에 ε이 오게 된다. B'기어에서 B,B'기어의 축 S_b와 S_b'의 중심을 연결하여 연장한 중앙선과 P_s점과의 중심각의 크기는

로서

이라 표시하면 l은 0 또는 소수이다. 제 1 도의 B'기어에서

즉, l=0이고, ε이 B'기어의 이빨이 두께 위에 놓일 때에는 이 끝원의 간섭범위 점 P_S가 결치기어의 작용시작점 S와 일치하여, 위에서 설명한 대로 A기어의 1번이나 B,B'기어의 2번 또는 A기어의 8번이나 B, B'기어의 8번 이빨을 낮추어 저치(低齒)로 해야 한다. 또 편의상 l이 0＜l＜0.5일 때에는 l=δ로 보고 0.5＜l＜1일 때에는 l-0.5=δ라 하면, B기어나 B'기어의 요동각의 크기θ는 이빨수 또는 핏치수로 표시하여 일반공식here

If the size of the fractional part except integer part is 0.155 = k

When k is 0 <k <0.5, the ε of the B gear is placed in the groove, not the gear teeth, and when it is in the range of 0.5 <k <1, the ε is placed on the tooth thickness. If k is smaller than 0.5, then k = ε. If k is larger than 0.5, k-0.5 = ε. Since it is above the groove and Z _b = Z _b ', it is excellent, so in the B' gear, ε is placed on this thickness in addition to the teeth. The size of the central angle between the center line and the point P _s extending from the B 'gear by connecting the centers of the axes S _b and S _b ' of the B and B gears is

as

Where l is zero or decimal. In B 'gear of FIG. 1

That is, when l = 0 and ε is the tooth of B 'gear over thickness, the interference range point P _S of this end circle coincides with the starting point S of the gear. Lower teeth of B 'gear 2 or 8 of A gear or 8 of B and B' gear should be lowered. For convenience, if l is 0 <l <0.5, l = delta, and if 0.5 <l <1, l-0.5 = δ, the swing angle θ of B gear or B 'gear is tooth or pitch General formula

θ = α + β-1-δ

It can be represented as.

However, as in the first diagram, if the point P _{s and the} point S coincide with l = 0 and δ = 0, if the deformation is applied to the haircut and the number 2 of the B, B 'gears or the number 1 of the A gears are lowered, the swing angle becomes one. As the pitch decreases, the above formula

θ = α + β-2

It becomes

Where θ = 8 + 4.31-2 = 10.31

to be. Of course, this is different from the above when only the eighth gear of the A gear is lowered. The actual swing angle θ ° is made to a certain level, but it is somewhat different depending on the backlash, the teeth profile, and the accuracy of the shaft spacing. When the to-gear gear A rotates in one direction, the pair of spur gears B and B 'inscribed therein have a swing angle θ ° and simultaneously swing in opposite directions.

Example 2

As shown in the second diagram, when two spur gears internally inscribed to A with Z _a = 24 have different sizes, the number of teeth of B gear is Z _b = 14 and the number of teeth of gear C is Z _c = 10, B interference range of the kkeutwon of gears and P _e and P _s When "the central angle size between points β _1, a gear and the C gears and interference range P _s and P _e of" the central angle size between points d β ₂ β The general formula to find β ₁ ≒ 5.17, β ₂ ≒ 3.59 and the maximum number of teeth α _x that can be left on the A gear is modified as follows.

Α _x = 8.

When A turns to R and tooth 8 pushes tooth 8 of gear B to the point P _e , gear B stops and the tooth positions are as shown in FIG.

로서 k=0.585＞0.5임으로, B기어와 C기어의 축 S_b와 S_c의 중심을 연결하여 연장한 중앙선이 B기어의 11번 이빨이 두께위에 놓인다. 즉, ε=k-0.5=0.585-0.5=0.085이고 Z_b, Z_c둘다 우수임으로 C기어에서는 중앙선이 홈 위에 놓이게 된다.In B gear

As k = 0.585> 0.5, the center line extending by connecting the centers of the shafts S _b and S _c of the B gear and the C gear is placed on the thickness of the 11th tooth of the B gear. That is, ε = k-0.5 = 0.585-0.5 = 0.085 and Z _b and Z _c are both excellent, so the center line is placed on the groove in C gear.

이며,

인데, 소수부분 l=0.71로서 δ=l-0.5=0.21이다. 그럼으로 B,C기어가 정지된 상태에서 A기어는 R방향으로 더 돌아서 1번 이빨이 P_s점을 지나 δ=0.21핏치 더 돌아가서 C기어의 1번 이빨과 만나는 작용시작점 S점이 생기게 된다. 이 경우 어느 기어든지 변형을 가해 저치로 만들 필요는 없다. A기어가 계속 돌아서 C기어를 R방향으로 돌려서 C기어가 정지할 때 까지의 중심각의 크기를 θ_C라 하면In C gear

Is,

The fractional part l = 0.71, where δ = l-0.5 = 0.21. Thus, while the gears B and C are stopped, the gear A rotates further in the R direction so that tooth 1 passes through the point P _s and then turns δ = 0.21 pitches further to meet the point S of the tooth of the gear C. In this case, it is not necessary to deform any gear to make it low. When the gear A keeps turning and the gear C rotates in the R direction until the gear C stops, the size of the center angle is θ _C.

가 되어 이때의 θ_b와 θ_c는 이빨수 또는 핏치수로서는 같은 수치이나, 각도로 표시하면 θ_c°＞θ_b°가 된다. 그런데, A기어와 C기어의 맞물림이 끝나고, A기어가 R방향으로 더 돌아서 B기어와 첫 접촉 작용이 시작될 때를 살펴보면However, at this time, the B gear may have returned to the L direction, and the center angle of rotation θ _b of the B gear is

Θ _b and θ _c at this time are the same value as teeth or pitch, but are expressed as θ _c °> θ _b ° when expressed in degrees. By the way, when the A gear and the C gear are engaged, the A gear turns further to the R direction and the first contact with the B gear starts.

임으로 l_c=0.29로서 δ_c=0.29라 할 수 있어, B기어의 13번 이빨의 이 두께위에 P_s'점이 오게되어, A기어의 1번이 B기어의 13번 이빨을 밀지 못하고 걸리게 된다. 그럼으로 이와같이 A기어가 C기어와는 원활히 작용하나, B기어와는 걸려서 회전력을 전달할 수 없을 때는 l_c=0.29와 δ=0.21의 크기를 참작하여 A기어의 1번과 8번 이빨의 높이를 알맞게 낮추어 이상적인 동작이 나오도록 해야 한다. 더욱이나 β₁-β₂≥1 임으로, A기어의 1번 이빨이 B 및 C 기어와 매번 다른 이빨에서 첫 접촉작용이 일어나 제네바 스톱 작용을 하는 캠을 부차할 수 없다. 따라서, 이와같이 B,C기어가 중심각의 크기가 다른 요동각을 지니고, 요동하면서 서서히 반대방향으로 돌아가는 특이한 요동출력이 필요할 때에는 클릭(click)과 래치트 휠(ratchet wheel)을 부착하거나, 별도의 특수 캠 장치를 부착하여 사용해야 한다.Since k _c = 0.795 and k _c > 0.5, in this case the centerline will be the tooth on the C gear above the thickness or ε _c = k _c -0.5 = 0.795-0.5 = 0.295. At this time, in gear B

Therefore, l _c = 0.29 and δ _c = 0.29, so that the point P _s ' is placed on the thickness of tooth 13 of the B gear, so that the number 1 of the A gear does not push the 13 teeth of the B gear. Therefore, when A gear works well with C gear, but it cannot engage with B gear and cannot transmit rotational force, the height of teeth 1 and 8 of A gear is increased by taking into account the size of l _c = 0.29 and δ = 0.21. You should lower it down properly to get the ideal behavior. Furthermore, since β ₁ -β ₂ ≥ 1, the first tooth of the A gear is in contact with the B and C gears every other time, so that the cam that acts as a Geneva stop cannot be secondary. Therefore, when the B and C gears have swing angles with different center angles, and need a unique swing output that rotates slowly in the opposite direction while attaching a click and a ratchet wheel, Cam device must be attached.

Example 3

As shown in Fig. 3, a pair of spur gears B and B 'are internally engaged with the toothed gear A, or Z _a > 2Z _b , so that B and B' do not bite directly, but a single gear train is provided through the spur gears C and D. In order to form a gear train, you can obtain a swing output with several swing angles.If you place another small spur gear E in the center of gear A as shown in the 3rd figure, The gears can also achieve left and right rotational movements with large swing angles of several rotations.

Example 4

If the same spur gears B ₁ , B ₂ , B ₁ 'and B ₂ ' are inscribed with each other on the internal toothing gear A as shown in Fig. 4, two pairs of opposite swing outputs, namely B ₁ , B ₁ 'and You can get the movement of B ₂ , B ₂ '. In this case, the maximum number of teeth α _x that can be left on the A gear is

Where x is the number of inscribed gears and x pairs.

에서

가 되어

는 무한 소수임으로 이빨수 선정을 근사치에서 찾아야 한다. 또 제 2 도와 같이 A기어에 x개 만큼의 기어 이빨 있는 부분 α와 α'를 만들어도 되며, Z_b1=Z_b1'≠Z_b2=Z_b2'되게 하여도 된다.Becomes In this case, the pitch circle diameter of A gear is called D, and the diameters of the four inscribed gears are d.

in

Become

Since is an infinite prime number, the tooth number selection should be approximated. In addition, as in the second diagram, the parts α and α 'having x gear teeth as many as A gears may be made, and Z _b1 = Z _b1 ' ≠ Z _b2 = Z _b2 '.

As seen in the above embodiments, since some of the teeth of the internal gear are removed, the wear of the remaining teeth, that is, the first and αth teeth of the α teeth, is a problem. In order to reduce the inertia of the swing gear shaft, which is an output gear, it is recommended to take supplementary measures such as using a spring or stopping the output shaft completely by applying a Geneva stop mechanism. For the first contact between the gears and the spur gears, which are output swing gears, the first or αth teeth of the gears will be lowered so that the contact will begin at the point of action close to the line of action of the normal gear. .

In addition, it is common to inscribe a pair of ordinary spur gears in a symmetrical position in the center of a toothed out gear, but it leaves α teeth less than α _{x in the} A gear, and accordingly, the B 'gear is placed in a position not symmetric to the B gear If internally engaged with B and B 'gears, hepatic pulsating movements with a long stop time can be obtained for each cycle of the swing output gear. If you use the internal gear to switch from the rotational motion to the swinging motion, you can get bigger swinging angle than when the spur gear is circumscribed. Robert et al. Will be widely used, especially for light load applications.

Claims (2)

Two or more spur gears interlocked with each other are inscribed to the toothed internal gear which has removed more than half of the teeth of the internal gear and rotated in one direction by using the internal toothed gear as a cylindrical rotational input. How to convert the rotational motion to the rocking motion using the gear to make the rocking output of the output. The method of claim 1, wherein two internal gears are not directly engaged with each other, and a plurality of swing motions are generated by forming a gear train using superior connection gears therebetween.

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