CN215529789U - Rake tooth arrangement structure of power-driven rake - Google Patents
Rake tooth arrangement structure of power-driven rake Download PDFInfo
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- CN215529789U CN215529789U CN202121058502.1U CN202121058502U CN215529789U CN 215529789 U CN215529789 U CN 215529789U CN 202121058502 U CN202121058502 U CN 202121058502U CN 215529789 U CN215529789 U CN 215529789U
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Abstract
The utility model discloses a rake tooth arrangement structure of a power-driven rake, which comprises a gear box and 2n groups of rake groups, wherein n is more than or equal to 1, the gear box comprises gears and rake tooth shafts which are arranged side by side and are meshed with each other, a rake tooth seat is arranged at the lower end of each rake tooth shaft, each rake group comprises 2 rake teeth fixed on the corresponding rake tooth seat, the rake tooth shafts are arranged side by side, the gears are sleeved on the rake tooth shafts, the gears drive the rake tooth shafts and the rake teeth to rotate, and the rotation direction of the rake tooth shafts is consistent with the blade directions of the 2 rake teeth on the same rake tooth shaft; the rotation directions of the adjacent rake tooth shafts are opposite, and the rake teeth on the adjacent rake tooth seats are closely and alternately arranged. The harrow teeth on adjacent harrow tooth seats are closely and alternately arranged, the vibration borne by the rack is uniformly dispersed, the machine operates stably, the pressure borne by the machine is smaller, and the relative load oil consumption is reduced; the peak torque of the frame is smaller, and the oil consumption is correspondingly smaller.
Description
Technical Field
The utility model relates to a working part of a tillage implement with a driving type rotary working part, in particular to a rake tooth arrangement structure of a power driving rake.
Background
The power-driven harrow is a machine tool which drives a working part to carry out dry land soil crushing and soil preparation operation by utilizing a power output shaft of a tractor and through a universal joint transmission shaft and a transmission system. The main working part is a row of rake tooth shafts, the lower ends of the rake tooth shafts are provided with rake tooth seats, and each rake tooth seat is provided with two rake teeth. When the soil-loosening plough is in work, the harrow toothed shaft is driven by the power output shaft through the transmission system, rotates and advances to impact soil blocks, so that plough layer soil is loosened.
The prior art with the patent name of CN208783177U discloses a deep scarification power driven harrow, which comprises a traction frame arranged on a rotor gear box, wherein the top end of the rotor gear box is provided with a gear box, the rotor gear box is provided with a plurality of groups of rotor gears and harrow teeth shafts which are mutually connected, the lower end of each harrow teeth shaft is provided with a harrow teeth seat, each harrow teeth seat is provided with at least two harrow teeth, and the rotor gears are connected with an output gear of the gear box; when the gear box is in work, the gear box input shaft drives the gear box to work, the gear box output gear in the gear box rotates to drive the rotor gear arranged on the rake tooth shaft to rotate, and the rotor gear rotates to drive the rake teeth to horizontally rotate at a high speed; as can be seen from the description and the attached fig. 4, the rake teeth on the adjacent rake tooth shafts are arranged in a 90-degree staggered manner; the peak torque of the harrow teeth during the soil penetration is too high, the pressure of the machine frame and the tractor is too high, and the oil consumption of the tractor during the work is correspondingly increased.
SUMMERY OF THE UTILITY MODEL
The utility model provides a rake tooth arrangement structure of a power-driven rake, which solves the problems of overlarge pressure and overlarge oil consumption of machines and tractors caused by overhigh peak torque when rake teeth are buried in the soil in the prior art; the technical scheme is as follows:
a rake tooth arrangement structure of a power-driven rake comprises a gear box and 2n groups of rake groups, wherein n is more than or equal to 1, the gear box comprises gears and rake tooth shafts which are arranged side by side and are meshed with each other, a rake tooth seat is arranged at the lower end of each rake tooth shaft, each rake group comprises 2 rake teeth fixed on the corresponding rake tooth seat, the rake tooth shafts are arranged side by side, the gears are sleeved on the rake tooth shafts, and the gears are arranged in the gear box; the rake teeth comprise back parts and blade parts with blades, the rake tooth shaft drives the rake tooth seat and the rake teeth to rotate, and the rotation direction of the rake tooth shaft is consistent with the blade parts of 2 rake teeth on the same rake tooth shaft in direction; the rotation directions of the adjacent rake tooth shafts are opposite, and the rake teeth on the adjacent rake tooth seats are closely and alternately arranged.
Compared with the traditional 90-degree staggered arrangement, the rake teeth on the adjacent rake tooth seats are closely and staggered arranged, the vibration borne by the rack is uniformly dispersed, the machine operates stably, the pressure borne by the machine is lower, and the relative load oil consumption is reduced; the peak torque of the frame is smaller, and the oil consumption is correspondingly smaller; the pressure born by the soil is balanced and is uniformly distributed, so that the stability of the machine is better.
And the harrow teeth on adjacent harrow tooth seats are closely and alternately arranged, so that the soil is crushed more uniformly, and the effect is better.
Preferably, the distance between every two adjacent rake tooth shafts is 1.02-1.1 times of the diameter of the rake tooth seat; preferably, the distance between every two adjacent rake tooth shafts is 1.02-1.04 times of the diameter of the rake tooth seat; further preferably, the distance between the adjacent rake tooth shafts is 1.02 times of the diameter of the rake tooth seat; smaller spacing helps to better distribute torque, reduce power; and simultaneously, better soil operation effect can be generated.
The preferred installation angle of the rake teeth is that the rake teeth on the rake teeth shaft rotating clockwise deviate from the plane vertical to the traction direction by an angle smaller than 45 degrees; still further preferably, the rake teeth on the rake tooth shaft rotating clockwise deviate from a plane perpendicular to the pulling direction by an angle of less than 30 °; even more preferably the tines on the clockwise rotating tine shaft are offset by less than 15 from a plane perpendicular to the direction of drag.
The rake teeth on the rake tooth shaft rotating clockwise are arranged on or close to the plane perpendicular to the pulling direction to reduce the torque, thereby reducing the oil consumption and prolonging the service life of the machine tool.
Preferably, the number of tines on the tine block is greater than 2.
The utility model has the beneficial effects that:
compared with the traditional 90-degree staggered arrangement, the rake teeth on the adjacent rake tooth seats are closely and staggered arranged, the vibration borne by the rack is uniformly dispersed, the machine operates stably, the pressure borne by the machine is lower, and the relative load oil consumption is reduced; the peak torque of the frame is smaller, and the oil consumption is correspondingly smaller; the pressure born by the soil is balanced and is uniformly distributed, so that the stability of the machine is better;
arranging the rake teeth on the rake tooth shaft rotating clockwise on a plane perpendicular to the traction direction or close to the plane perpendicular to the traction direction so as to reduce the torque, thereby reducing the oil consumption and prolonging the service life of the machine tool;
the rake teeth of the power-driven rake are arranged in the following arrangement structure: the rake teeth on adjacent rake tooth seats are arranged in a closely staggered manner, and the rake teeth on the clockwise rotating rake tooth shaft are arranged on a plane perpendicular to the drawing direction or close to a plane perpendicular to the drawing direction; the special angle arrangement is adopted, the distance between every two adjacent rake tooth shafts is reduced, the distance between every two adjacent rake tooth shafts is 1.02-1.1 times of the diameter of the rake tooth seat, vibration borne by the rack is uniformly dispersed as far as possible, the machine runs more stably, the torque peak value is reduced as far as possible, and oil consumption is reduced to the maximum extent.
Drawings
FIG. 1 is a schematic structural view in elevation of a tine arrangement of a power driven rake in accordance with the present invention;
FIG. 2 is a schematic structural view of the bottom view of FIG. 1;
FIG. 3 is a partial view of FIG. 2;
FIG. 4 is a schematic structural view of the top view of FIG. 1;
FIG. 5 is a schematic structural view taken along line A-A in FIG. 1;
fig. 6 is a tine arrangement of a prior art power driven rake.
In the figure: 1. rake teeth B and 2, a gear box 3, rake teeth A and 4, a rake tooth shaft 5, rake teeth C and 6, a gear 7, a rake tooth seat 8, a box-type oil seal 9, a felt ring 10 and an O-shaped sealing ring.
Detailed Description
As shown in fig. 6, in the prior art, the rake teeth on adjacent rake tooth shafts are staggered by 90 °.
Example 1
Referring to fig. 5, the rake teeth arrangement structure of the power driven rake of the present invention is further described with reference to fig. 1 to 5, and the rake teeth arrangement structure of the power driven rake comprises a gear box 2 and 2n groups of rake groups, wherein n is greater than or equal to 1, the gear box 2 comprises a gear 6 and a rake teeth shaft 4 which are arranged side by side and are engaged with each other, a rake teeth seat 7 is arranged at the lower end of the rake teeth shaft, and the gear 6 is sleeved on the rake teeth shaft 4; referring to fig. 3, the rake group includes a rake tooth a3 and a rake tooth C5 fixed to the rake tooth base 7; the gears on the adjacent rake tooth shafts 4 are meshed, and the gear 6 is arranged in the gear box 2; the rake teeth comprise back parts and blade parts comprising blades, the rake teeth A3 and the rake teeth C5 are mounted at the lower end of the rake teeth shaft 4 through a rake teeth seat 7, a gear 6 drives the rake teeth shaft 4 to rotate, the rake teeth shaft 4 drives the rake teeth A3 and the rake teeth C5 to rotate, and the rotation direction of the rake teeth shaft 4 is consistent with the blade parts of the rake teeth A3 and the rake teeth C5 on the same rake teeth shaft in orientation; the rotation directions of the adjacent rake tooth shafts are opposite, the rake tooth shafts 4 are arranged side by side, and the rake teeth A3 and the rake teeth B1 on the adjacent rake tooth seats 7 are closely and alternately arranged; the rake teeth a3 and B1 of the adjacent rake teeth seats 7 are arranged in a staggered manner in close proximity without interfering with each other.
Referring to fig. 3, the distance L between adjacent rake teeth is 1.02 times the diameter D of the rake teeth seat, and when the diameter D of the selected rake teeth seat is 240mm, the distance L between adjacent rake teeth is 245 mm.
Referring to fig. 1-4 in combination, the rake shaft, which rotates clockwise in fig. 4, rotates counterclockwise in fig. 2 and 3;
in connection with fig. 3 and 4, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (fig. 3) of less than 45 °.
As shown in fig. 5, the rake teeth shaft 4 and the rake teeth base 7 are made into an integral structure by die forging, and the strength of the integral structure is higher; the rake teeth shaft 4 and the rake teeth base 7 may be of a separate structure and fixed together by welding or other connection methods.
Referring to fig. 5, the lower end of the rake pinion 4 uses a double-row tapered roller bearing, which has multi-axial impact resistance, high load capacity and a service life 30% longer than that of the conventional tapered roller bearing; by adopting the O-shaped sealing ring 10, the box-shaped oil seal 8 and the felt ring 9 to combine labyrinth seal, multiple seals can effectively prevent water and soil from permeating into the rotor and the gear box.
Example 2
On the basis of example 1, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (fig. 3) of less than 30 °.
Example 3
On the basis of example 1, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (fig. 3) of less than 15 °.
Example 4
On the basis of the embodiment 1, the distance L between the adjacent rake teeth shafts is 1.04 times of the diameter D of the rake teeth seat, and when the diameter D of the selected rake teeth seat is 240mm, the distance L between the adjacent rake teeth shafts is 250 mm.
Referring to fig. 4 and 3 in combination, the rake teeth on the rake shaft rotating clockwise in fig. 4 are offset from the plane perpendicular to the direction of drag by an angle α (as in fig. 3) of less than 45 °.
Example 5
On the basis of embodiment 4, with combined reference to fig. 4 and 3, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (see fig. 3) of less than 30 °.
Example 6
On the basis of embodiment 4, with combined reference to fig. 4 and 3, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (see fig. 3) of less than 15 °.
Example 7
On the basis of the embodiment 1, the distance L between the adjacent rake teeth shafts is 1.1 times of the diameter D of the rake teeth seat, and when the diameter D of the selected rake teeth seat is 240mm, the distance L between the adjacent rake teeth shafts is 264 mm.
Referring to fig. 4 and 3 in combination, the rake teeth on the rake shaft rotating clockwise in fig. 4 are offset from the plane perpendicular to the direction of drag by an angle α (as in fig. 3) of less than 45 °.
Example 8
On the basis of embodiment 7, with combined reference to fig. 4 and 3, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (see fig. 3) of less than 30 °.
Example 9
On the basis of embodiment 7, with combined reference to fig. 4 and 3, the rake teeth on the rake tooth shaft rotating clockwise in fig. 4 deviate from the plane perpendicular to the pulling direction by an angle α (see fig. 3) of less than 15 °.
Claims (8)
1. A rake tooth arrangement structure of a power-driven rake comprises a gear box and 2n groups of rake groups, wherein n is more than or equal to 1, the gear box comprises gears and rake tooth shafts which are arranged side by side and are meshed with each other, a rake tooth seat is arranged at the lower end of each rake tooth shaft, each rake group comprises 2 rake teeth fixed on the corresponding rake tooth seat, the rake tooth shafts are arranged side by side, the gears are sleeved on the rake tooth shafts, and the gears are arranged in the gear box; the rake teeth comprise back parts and blade parts with blades, the rake tooth shaft drives the rake tooth seat and the rake teeth to rotate, and the rotation direction of the rake tooth shaft is consistent with the blade parts of 2 rake teeth on the same rake tooth shaft in direction; the rotation direction of adjacent harrow tooth axle is opposite, its characterized in that: the rake teeth on adjacent rake tooth seats are arranged in a closely staggered manner.
2. The tine arrangement of a power driven rake of claim 1, wherein: the distance between every two adjacent rake tooth shafts is 1.02-1.1 times of the diameter of the rake tooth seat.
3. The tine arrangement of a power driven rake of claim 2, wherein: the distance between every two adjacent rake tooth shafts is 1.02-1.04 times of the diameter of the rake tooth seat.
4. The tine arrangement of a power driven rake of claim 3, wherein: the distance between adjacent rake tooth shafts is 1.02 times of the diameter of the rake tooth seat.
5. The tine arrangement of a power driven rake of claim 1, wherein: the rake teeth on the rake tooth shaft rotating clockwise deviate from the plane perpendicular to the pulling direction by an angle of less than 45 deg..
6. The tine arrangement of a power driven rake of claim 5, wherein: the rake teeth on the rake tooth shaft rotating clockwise are offset by less than 30 from a plane perpendicular to the direction of draw.
7. The tine arrangement of a power driven rake of claim 5, wherein: the rake teeth on the rake tooth shaft rotating clockwise are offset by an angle of less than 15 deg. from a plane perpendicular to the direction of pulling.
8. The tine arrangement of a power driven rake of claim 1, wherein: the number of the rake teeth on the rake tooth seat is more than 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121058502.1U CN215529789U (en) | 2021-05-18 | 2021-05-18 | Rake tooth arrangement structure of power-driven rake |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202121058502.1U CN215529789U (en) | 2021-05-18 | 2021-05-18 | Rake tooth arrangement structure of power-driven rake |
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| CN215529789U true CN215529789U (en) | 2022-01-18 |
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| CN202121058502.1U Active CN215529789U (en) | 2021-05-18 | 2021-05-18 | Rake tooth arrangement structure of power-driven rake |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116438948A (en) * | 2023-04-22 | 2023-07-18 | 青岛郁金香机械有限公司 | Power-driven harrow |
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2021
- 2021-05-18 CN CN202121058502.1U patent/CN215529789U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116438948A (en) * | 2023-04-22 | 2023-07-18 | 青岛郁金香机械有限公司 | Power-driven harrow |
| CN116438948B (en) * | 2023-04-22 | 2024-01-26 | 青岛郁金香机械有限公司 | Power-driven harrow |
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