RU2209535C1 - Rotary working tool - Google Patents

Abstract

FIELD: agricultural engineering. SUBSTANCE: rotary working tool has disks and bushings with inclined bases mounted on horizontal polyhedral shaft. Receptacle surface for polyhedral shaft is formed in stop bushing. One of bushing bases has straight surface. Disks are equipped with teeth and positioned in angular offset relation with respect to one another on shaft. Disks are inclined with respect to shaft axis at an angle corresponding to inclination angle of bases of bushings joined thereto. Length of bushing and outer diameter of disk are determined from certain dependence. Operating surface of one tooth and non-operating surface of other tooth are arranged perpendicular to one another and have rounded portion of certain radius. EFFECT: wider operational capabilities, enhanced reliability in operation and provision for effective preparing of soil. 4 cl, 2 dwg

Description

 The invention relates to agricultural machinery, in particular to disk tillage implements.

 A device is known for pre-sowing soil preparation, containing an axis with a disk installed with the possibility of changing the angle (see USSR author's certificate 1678221, 5 A 01 B 29/04, 1989).

 A disadvantage of the known device is the presence of an additional disk made in the form of a truncated cone and connected to the main flat disk with a large base. The conical disk has a diameter smaller than the main flat disk and lies in the range m = 0.02 ... 0.03 m. For values of m <0.02 m, each additional disk compacts the surface soil layer, and for values of m> 0.03 m significantly increases the traction resistance of the working body (up to 40%).

In addition, the angle α between the generatrix and the base plane of the additional truncated cone is in the range of 35 ... 40 ^o , when these values are exceeded, the traction resistance to movement of the working body in the soil increases significantly (up to 30 ... 40%). The diameter of the main flat disk cannot be within 0.6 ... 0.7 m, because the diameter of the working body cannot provide high-quality soil preparation to the depth required by agricultural requirements.

 The closest known device in technical essence and the achieved result is a rotary working body containing a horizontal shaft mounted in bearings, having a drive in rotation, and on which disks are mounted obliquely relative to the axis of rotation of the shaft by means of spacer sleeves with inclined end bases, the angle the inclination of the disk to the axis is equal to the corresponding angle of inclination of the bases of the bushings mating with it (see USSR copyright certificate 1662377).

 A disadvantage of the known device is the implementation of the knives of the rotary working body in the form of ellipse disks, as well as the execution of the rotation shaft of two parts having a means of compensating for their angular displacements, which are located in the zone of the central bearing assembly between the ends of the shaft parts facing each other, interacting with each other through the specified tool.

In addition, the direction of the major axis of the ellipse of the disks should coincide with the corresponding major axis of the sleeve, and the angle of inclination of the disks to the axes of rotation of the shaft parts and the corresponding angle of inclination of the bases of the bushes should be 10 ... 30 ^o .

 However, the arrangement of knives of the rotary working body at smaller angles α leads to a sharp decrease in the lateral effect of the disk on the soil, and thus its crumbling decreases, and at large angles, the energy consumption for cultivating the soil increases sharply, it crumbles excessively, the machine experiences significant cyclic loads.

 The task of the invention is to expand the functionality, increase the reliability of the tool and the effectiveness of soil preparation during its processing.

 This goal is achieved in that the rotation shaft is made in the form of a polyhedron. Each spacer sleeve is made with a seating surface under the polyhedron. The end faces of the bushings mated to one another are made straight. The disks are equipped with teeth and are located relative to each other with angular displacement on the shaft of rotation.

The length of each spacer sleeve along the axis is determined by the expression
L = 0.5 (D • sinα + S),
where D is the diameter of the disk, m;
α is the angle of inclination of the disks to the axis of rotation, deg .;
S - disk thickness, m

где h - высота зуба, м;
n - число зубьев, шт.The outer diameter of each disk is determined by the expression

where h is the height of the tooth, m;
n is the number of teeth

The working surface of one tooth and the non-working surface of the other are perpendicular to each other and have a radius of rounding equal to
R ₁ = h ² / Rsinarccos (1-h / R),
where R is the radius of the disk.

 To match the declared object to the criterion of "significant differences", a search was conducted by cl. IPC 5 A 01 B 9/00, 49/02, 23/06, 29/04; IPC 6 A 01 8 9/00, 15/16, 33/08.

 As a result of the search, the applicant did not find technical solutions in which there are signs similar to those distinguishing the claimed solution from the prototype.

 The essence of the invention is illustrated by drawings. In FIG. 1 shows a general view of a rotating working body with the formation of a guide slit in the soil, FIG. 2 is a view A in FIG. 1 with a design diagram for determining the outer diameter of a gear disk.

 The rotary working body comprises a horizontal shaft 6 mounted in bearings 2, having a rotation drive 1, on which discs 5 are mounted, mounted obliquely with respect to the axis of rotation of the shaft 6, by means of spacer sleeves 3 with inclined end bases 4, the angle of inclination of the disk 5 to the specified axis is respectively the angle of inclination of the bases 4 of the associated bushings 3.

 The rotation shaft 6 is made in the form of a polyhedron, and in each spacer sleeve 3 a seating surface 10 is made for a polyhedron. Mating with each other end base 8 of the bushings 3 are made straight, the disks are equipped with teeth 9 and are located relative to each other with angular displacement on the shaft of rotation 6.

The length of each spacer sleeve 3 along the axis is determined by the expression
L = 0.5 (D • sinα + S),
where D is the diameter of the disk, m; α is the angle of inclination of the disks to the axis of rotation, deg., S is the thickness of the disk, m

где h - высота зуба, м; n - число зубьев, шт.The outer diameter of each disk 5 is determined by the expression

where h is the height of the tooth, m; n is the number of teeth

The working surface of one tooth and the non-working surface of the other are perpendicular to each other and have a radius of rounding equal to R ₁ = h ² / Rsinarccos (1-h / R).

 Figure 2 shows that the rotation shaft 6, shown in figure 1, is a polyhedron, for which, for example, a square shaft is used, and accordingly, the seating surface 10 of the spacer sleeves 3 has a square section.

A disk 5 is mounted between the inclined parallel bases 4 of the two spacer sleeves 3. In this case, the disks 5 and the sleeves 3 on the rotation shaft 6 are mounted relative to each other with angular mixing. For example, the shaft 6 is made square, while the disks 5 with spacer sleeves 3 are placed on the shaft 6 so that the position of the angle φ of rotation of the disks 5 relative to the mark of the radius of rotation of each subsequent disk 5 are located with an angular offset of 90 ^o .

Например, при заданном диаметре диска D=0,26 м, угле наклона дисков α= 15^o и толщине диска S=0,01 м определим по выражению L(м)=0,5•(D•sinα+S), осевой размер втулки 3 равен L=0,5•(0,26•sin15^o+0,01)=0,0386 м, т.е. 3,68 см.A mark of the radius of rotation of the disk is in the continuation of the side of the polyhedron 6. In figure 2 - the point is marked φ = 90 ^o , D is the diameter of the outer circumference of the teeth 9 of the disk 5, α is the angle of inclination of the disks 5 to the axis of rotation 6, L is the total assembly length axis (sleeve length + disc thickness + sleeve length). From the triangle ABC we define L (m) = D • sinα. Knowing the thickness of the disk S (m), we determine the length of each spacer sleeve by the expression

For example, for a given diameter of the disk D = 0.26 m, the angle of inclination of the disks α = 15 ^o and the thickness of the disk S = 0.01 m, we define by the expression L (m) = 0.5 • (D • sinα + S), axial the size of the sleeve 3 is L = 0.5 • (0.26 • sin15 ^o +0.01) = 0.0386 m, i.e. 3.68 cm.

The rotary working body allows you to install between the straight bases of 8 spacer sleeves 3 other spacer sleeves 7, the length of which is determined by the conditions of the design scheme for the formation of a guide gap AC in the soil. The number of gear discs 5 mounted on the shaft 6 is determined by the expression N _a (pcs.) = B _p / (L + CD), because In _p is the working width of the rotary working body, m, L is the width of the tillage slit L (m) = D • sinα + S, CD (m) is the specified roll width between the AC slots, then we determine the number of gear discs 5 N _a = B _p / (D • sinα + S + CD).

For example, In _p = 3.6 m, D = 0.26 m, α = 15 ^o , S = 0.01 m, CD = 0.15 m.

N _a = 3.6 / (0.26 • sin15 ^o + 0.01 + 0.15) = 15.8≈16 (pcs.)
Thus, the width (AS) of the tillage slit is L (m) = D • sinα + S = 0.26 • sin15 ^o + 0.01 = 0.077, i.e. equal to 7.7 cm. With a distance of CD between them of 15 cm, for a given working width (B _p ) of the rotating working body of 3.6 m, 16 discs 5 must be installed on shaft 6. diameter 26 cm

In the absence of rolls СD = 0 between the AC slots, i.e. continuous tillage, the number of gear discs 5 is respectively determined by the expression
N _a (pcs.) = B _p / (D • sinα + S) = 3.6 / (0.26 • sin15 + 0.01) = 47,
those. with continuous tillage, it is necessary to install 47 pcs on shaft 6. gear discs 5.

 When the shaft 6 is rotated, the gear disks 5, in addition to the rotational movement with a certain angular velocity, make oscillating movements both in the longitudinal plane and in the transverse plane with simultaneous cutting of the soil with each tooth 9 of the disk 5. Moreover, the sinusoidal vibrations of each disk 5 differ in phase , i.e. according to their angular displacement of the disks on the shaft 6. Simultaneously with the oscillatory movements of each disk 5, a buoyant force P appears on its lateral surface, which ejects crumbled soil on both sides of the plane of rotation of the disk, which improves mixing.

Figure 2 shows that R = D / 2 is the radius of the outer circumference of the teeth 9 of the disk 5, r is the inner radius, which is equal to r = Rh, where h is the height of the tooth 9. From the triangle 0GK we define the angle ψ as cosψ = r / R, replacing r = Rh in this expression, we obtain that cosψ = (Rh) / R or cosψ = 1-h / R. We determine the angle ψ for a given number of teeth (n) as ψ = 360 ^o / n. Therefore, cosψ = 1-h / R, whence the radius of the outer circle R of the teeth 9 of the disk 5 at a given tooth height (h) is determined by the expression
R = h / (1-cos360 ^o / n), m.

Since R = D / 2, then D = 2h / (1-cos360 ^o / n). For example, for a given tooth height h = 0.025 m, the number of teeth n = 10 pcs., We determine the diameter of the disk 5. D = 2h / (1-cos360 ^o / n) = 2 • 0.025 / (1-cos360 ^o / 10) = 0 , 26 m. Since cosψ = 1-h / R, then ψ = arccos (1-h / R) and l / R = sinψ, i.e., l = Rsinψ or l = Rsinarccos (1-h / R) and, therefore, the rounding radius is defined as the ratio of the squared tooth height (h) to its length (l), i.e. R ₁ = h ² / Rsinarccos (1-h / R) = 0.008 (m)
In FIG. 2 it is seen that when the rotation of the gear disk 5 with an angular velocity ω _a appears linear (tangential) speed V _a . The number of revolutions per unit time of the gear disk 5 when moving the traction means with a speed of V _{t is} determined from the condition of equality of speeds V _a = V _t .

где D - диаметр диска, м; N/t - число оборотов (с^-1=Гц.), L_a - длина внешней окружности диска, м.It is known that the linear velocity of a material point moving in a circle is determined by the formula

where D is the diameter of the disk, m; N / t is the number of revolutions (s ^-1 = Hz.), L _a is the length of the outer circumference of the disk, m.

Therefore, for V _t = L _a • N / t, we have N / t = V _t / L _a .

For example, with D = 0.26 m, we get L _a = π • D = 3.14 • 0.26 = 0.817 m. The number of revolutions N (s ^-1 ) = V _t / 0.817, at a speed of movement V _t = 11 , 7 km / h = 3.25 m / s we get / N (s ^-1 ) = 3.25 / 0.814 = 3.97 or the number of revolutions of the gear 5 in one minute N = 3.97 • 60 = 239 rpm min

 Thus, the number of revolutions of the gear disk 5 should correspond to the selected technological speed of movement of the machine-tractor unit when processing the soil.

 Rotational working body operates as follows.

 When the tillage implement moves, the inclined disks 5 located on the rotation shaft 6 in the longitudinal and transverse planes at different angles receive rotation from the drive 1, cut into the formation and, making oscillating movements during rotation in both planes, carry out undercutting of the teeth 9 with a sine law crumble it and carry out the ejection of different fractions of the soil from under each disk 5 due to the emerging force (P) directed perpendicular to the plane of the gear disk, and the centrifugal force of each cutting surface of the tooth 9.

 A rotary working body, designed for the formation of a soil-forming AS gap to a certain depth (H), during its rotation, transfers different fractions of the soil and plant residues from under each disk 5.

 A rotary working body, designed for continuous loosening of the soil (EF) to a certain depth, during its rotation, actively loosens the soil layer, in which each disk 5 transfers different fractions of the soil and plant residues from one soil-forming gap formed by one disk 5 to another , i.e. another drive. At the same time, larger fractions of the soil and plant debris are placed at the bottom of each slot, and smaller fractions of the soil fill the fractions from above.

 A ridge is formed between each disk (the formation of a soil-forming gap) after their 5th movement, i.e. between each soil-forming AC gap, heavier soil fractions are carried onto the surface of the CD formation, which are sprinkled with lighter soil fractions.

 As a result of the fact that the disks 5 with the sleeves 3 are mounted on a multifaceted rotation shaft 6 at a certain angle α to the axis of rotation in the longitudinal direction and are located relative to each other with an angular displacement φ on the rotation shaft in the transverse direction, balancing the oscillations along the rotation axis of the rotational worker body, which not only reduces the load on the bearings 2, but also improves the quality with various technologies for pre-sowing tillage.

Claims (4)

 1. A rotary working body, comprising a horizontal shaft mounted in bearings, having a rotational drive, on which disks are mounted obliquely with respect to the axis of rotation by means of spacer sleeves with inclined end bases, and the angle of inclination of the disk to the specified axis is equal to the corresponding angle of inclination of the bases mated to bushings, characterized in that the rotation shaft is made in the form of a polyhedron and in each spacer sleeve there is a seating surface under the polyhedron, while with each other, the end bases of the bushings are made straight, the disks are equipped with teeth and are located relative to each other with angular displacement on the shaft of rotation. . 2. A rotary actuator according to claim 1, characterized in that the length of each sleeve along the axis defined by the expression L = 0,5 (D sinα + S .), M, where D - diameter of the disk, m; α is the angle of inclination of the disks to the axis of rotation, deg. ; S - disk thickness, m 3. The rotary working body according to claim 1, characterized in that the outer diameter of each disk is determined by the expression D = 2 ^. h / (1-cos360 ^o / n), where h is the height of the tooth, m; n is the number of teeth 4. A rotary actuator according to Claim. 1, characterized in that the working surface of a tooth and a non-operating surface of the other are perpendicular to each other and have a radius of curvature equal to R ₁ = n ² / ^R. sin arccos (1-h / R), where R is the radius of the disk, m.

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