JPH026940B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a device that mutually converts rotational motion and reciprocating motion.

[Prior Art] It is often necessary to convert rotational motion into reciprocating motion, or conversely, converting reciprocating motion into rotary motion.
Rotating swash plates, rocking plates, and many other mechanisms have been used for a long time.

[Problems to be solved by the invention] However, these conventional mechanisms have shape constraints,
A conversion mechanism that is ideal in terms of efficiency, balance, etc. has not necessarily been realized. Various compressors, pumps, internal combustion engines, Stirling engines, etc. are compact, have a large load capacity, are smooth, have low contact pressure on sliding parts, have force balance, and have a relationship between rotation angle and displacement. Although a rotary/reciprocating motion converting device with a high degree of freedom is desired, there has been no device available that fully satisfies these demands.

The present invention is a rotary/reciprocating motion converter that is small in size, has a large load capacity, has a degree of freedom in the conversion relationship, and is balanced, and can be used in various compressors, pumps, internal combustion engines, Stirling engines, and other mechanisms. is intended to provide.

[Means for Solving the Problem] Corresponding to this object, the rotation/reciprocating motion conversion device using a guide groove of the present invention has a sine waveform or other smooth curve with n periods per revolution on the outer or inner surface of the cylindrical shape. m guide grooves with the same waveform that are displaced in the axial direction according to the circumferential angle are provided with a phase difference of α ₁ , α ₂ ...α _n , respectively, and a roller or ball that rolls along the guide groove is provided. n×m pistons are held at their respective positions and freely rotated, and the rotational motion of the cylindrical surface is converted into the reciprocating motion of the piston, or the reciprocating motion of the piston is converted into the rotational movement of the cylindrical surface, or the inverse relationship thereof. In a mutual conversion device between reciprocating motion and rotary motion between the cylindrical surface and the piston, which realizes a conversion action including speed change in a differential relationship that allows rotation of the piston, the phase difference α ₁ between each guide groove, α ₂ …Difference in phase difference between each adjacent groove of α _n | α ₂
It is characterized in that the difference between −α ₁ | and |α ₃ −α ₂ |…|α ₁ −α _n | is set to maintain a difference greater than a value corresponding to the groove width.

[Operation] Motion is transmitted between the cylindrical surface and the piston via the roller or ball between the guide groove on the cylindrical surface and the piston, and the rotational motion of the cylindrical surface is converted into linear motion of the piston, or vice versa. When the rotation of the piston is performed and the rotation of the piston is allowed, the piston moves linearly while rotating, and the conversion that causes a differential movement with the movement of the cylindrical surface is performed.

[Example] The present invention will be described below with reference to FIGS. 1, 2, 3, and 4.
The transmission of power and motion in the rotation of a cylindrical surface having a guide groove and the reciprocating motion of a piston having a roller or ball at a fixed position according to the embodiment shown in FIGS.

The cylindrical surface 1 has a guide groove 2 whose phase is the circumferential angle.
and 2' are provided in a sinusoidal waveform with two cycles per rotation, and are configured to be rotatable while being restrained from moving in the axial direction by thrust bearings 4 and 4' that support the shaft 3, and a piston is provided in each guide groove. Rollers 6, 6', 7 and 7' which are free to rotate around the radial direction of the piston provided in the piston 5 are fitted to the outer periphery of the piston 5 in order to suppress the rotation of the piston relative to the cylinder 8. Grooves 10 and 10' for the rollers 9 and 9' are provided. In response to the rotation of the shaft 3, the piston 5 rotates on the rotation surface 1.
A reciprocating motion is produced at a ratio of two reciprocations per rotation. The guide groove rotates 2 times per revolution as shown in Figure 3, which shows the cylindrical surface unfolded.
Four intersections are generated per period, but by shifting the phase of each guide groove by an angle corresponding to the groove width from (1/2)π, it is possible for both pairs of rollers in each guide groove to enter the intersection at the same time. Make sure not to. While the pair of rollers is in the intersection, the piston 5 receives force and motion from the remaining pair of rollers.

The contact between the rollers 6 and 6', 7 and 7' and the guide grooves 2 and 2' is in line contact as shown in FIG.
It rolls in contact with one side of the guide grooves 2 and 2', and is further rotatably supported by a small ball 12 against the piston 5 with only rolling friction similar to a rolling bearing. Furthermore, as shown in FIG. 4b, the rolling balls 13 can be used in place of the rollers 6, 6', 7, and 7', and the guide grooves 2b can be shaped accordingly.
Furthermore, in order to reduce the slippage in the rollers, the rollers 6, 6', 7, and 7' are formed into a conical shape with a portion 13' in contact with the guide groove 2c having a height equal to the radius of the cylindrical surface, as shown in Fig. 4c. You can also.

If there are two guide grooves in this device, it is necessary to give (α ₂ - α ₁ ) a phase difference equivalent to the width of the groove or more, and to prevent the deviation from π/(m・n) from becoming too large. It's easy to do. As long as (α ₂ − α ₁ ) is equal to or larger than the groove width, two pairs of rollers will not enter the intersection of the guide grooves at the same time, and (α ₂ − α ₁ )
As long as is not extremely large, equilibrium can always be maintained.
That is, in the case of m=2 and n=2, α ₂ −α ₁ ≪
(π/4) can be easily made. This satisfies the condition for maintaining equilibrium.

Next, to describe the relationship between the allowable range of the phase difference θ equivalent to the groove width and the phase difference of the groove, as shown in Fig. 5a, when n = 1 and the number m of the guide grooves is 3, the groove Let θ be the phase difference in the circumferential angle corresponding to the width, and α ₁ , α ₂ ,
If α ₃ is x, x+n ₁ θ, x+n ₂ θ and n ₂ > n ₁ , it is necessary to set n ₂ −n ₁ = n ₁ −0, and n=2n ₁ ,
α ₁ + α ₂ + α ₃ = 360°, that is, 3x + 3n ₁ θ = 360°,
Assuming n ₁ =1, approximately optimal values of θ and x are found. In this case, there is a degree of freedom as θ≦40°, and generally, _θ has a margin of α ₁ ,
α ₂ and α ₃ can be selected.

When m=4, there are 12 intersections in one period as shown in FIG. 5b, and the degree of freedom in selection is reduced. When n=1, α ₁ , α ₂ , α ₃ , α ₄ are x, x+n ₁ θ,
x+n ₂ θ, x+n ₃ θ as n ₁ > n ₃ > n ₂ as n ₃ −
For example, let n ₂ , n ₁ −n ₂ , n ₃ −0, n ₁ −0 be 1, 2,
If you choose unequal integers like 3 and 4, n ₁ = 4, n ₂ = 2, n ₃ =
It becomes 3. Therefore, 4x+9θ=360°, and θ=
If 16°, α ₁ = 54°, α ₂ = 118, α ₃ = 86°, α ₄ =
It becomes 102°. In this case, θ=16° is generally a value close to the limit, and there is little room for free selection.

Note that the embodiment described above is for a case in which the piston is restrained by the cylinder and only linear movement is allowed, but if the structure is such that it also allows rotational movement of the piston, the rotation between the cylindrical surface and the piston In addition to the kinematic-linear or vice versa conversion movement, an intermediate conversion movement is realized, ie a conversion movement with a differential between the cylindrical surface and the piston.

In this way, the present invention aims to avoid overlapping of the groove intersections as much as possible, while minimizing the maximum phase difference and its deviation as much as possible to improve the smoothness and balance in the transfer of force between the cylindrical surface and the piston. Can be done.

[Effects of the Invention] In the present invention, by increasing the phase difference in the circumferential angle corresponding to the groove width, it is possible to increase the diameter and number of balls that enter the groove. load capacity can be increased. In addition, in the present invention, the conversion of motion between the cylindrical surface and the piston is
In addition to converting between rotational motion and linear motion, the piston in the middle can perform rotational motion and linear motion at the same time to achieve a transformation that has a differential relationship with the cylindrical surface. The degree of freedom is extremely large. Moreover, all the load portions of motion transmission can be achieved by rolling contact, resulting in smooth motion conversion.

Furthermore, in the present invention, the phase difference (α ₁ −α ₂ ) between the circumferential angles of the guide grooves can be made as small as possible to maintain balance.

As described above, according to the present invention, a plurality of rollers or rolling balls can be smoothly balanced and effectively utilized in converting rotation and reciprocating motion using the guide groove.

[Brief explanation of drawings]

FIG. 1 is an explanatory longitudinal cross-sectional view of the rotation/reciprocating motion conversion device, FIG. 2 is a cross-sectional view of the − part in FIG. 1, and FIG. 3 is an expanded explanatory view showing two guide grooves on the cylindrical surface.
FIG. 4 is a cross-sectional partial explanatory diagram showing the engagement state of the roller and the ball, FIG. 5 a is an explanatory diagram showing the phase relationship of the guide grooves, and FIG. 5 b is an explanatory diagram showing the phase relationship of other guide grooves. It is. 1... Cylindrical surface, 2, 2'... Guide groove, 3... Shaft,
5... Piston, 6, 6', 7, 7'... Roller,
8...Cylinder, 9,9'...Roller, 10,1
0'...Groove, 12...Small ball, 13...Rolling ball.

Claims (1)

[Claims] 1. m guide grooves with the same waveform on the outer or inner surface of a cylindrical shape with n cycles per revolution, such as a sinusoidal waveform or other smooth curve, which is displaced in the axial direction according to the circumferential angle,
The phase difference of the circumferential angle is set as α ₁ , α ₂ ...α _n , respectively, and the roller or ball n rolling along the guide groove is
×m pistons are held at their respective positions and freely rotated, and the rotational motion of the cylindrical surface is converted into the reciprocating movement of the piston, or the reciprocating movement of the piston is converted into the rotational movement of the cylindrical surface, or the inverse relationship thereof. In a mutual conversion device between reciprocating motion and rotary motion between a cylindrical surface and a piston that realizes a conversion action including speed change in a differential relationship that allows rotation of the piston, the phase difference α ₁ , α between each guide groove. ₂ ...Difference in phase difference between each adjacent groove of α _n |α ₂ −α ₁ |, |α ₃ −α ₂ |…
A rotation/reciprocating motion conversion device using a guide groove, characterized in that each difference of |α ₁ −α _n | is set to maintain a difference greater than a value corresponding to the groove width.