SU1351770A1 - Percussive power nut-setter - Google Patents

Abstract

The invention relates to a mechanized tool for assembling and disassembling threaded connections. The purpose of the invention is to simplify the design and increase reliability due to the smooth operation of the mechanism for controlling the impact geometry. The impact wrench co-, holds the composite body of parts 1 and 2, the anvil 4 with the working cam (О 1C

Description

5, a composite drummer comprising a leading part 9 connected through a safety coupling 8 to an output shaft 7. In the leading part 9 an intermediate element 3 is engaged with the work cams 14 and a conical surface 15, the side grooves are made in the leading part 9 which form an angle j5, which interact with the rollers 18 with a conical end, in the leading part 9 is placed a separator 16 with inclined radial grooves 17, the surfaces of which interact with

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The invention relates to a mechanized tool for assembling and disassembling threaded connections and can be used for assembly and installation work in various parts of the industry.

The purpose of the invention is to simplify the design and increase reliability due to the smooth operation of the mechanism for controlling the impact geometry,

FIG. 1 shows a impact wrench, longitudinal section J in FIG. 2, section A-A in FIG. 1; FIG. 3 is a sectional view BB in FIG. 1; FIG. 4 shows the mutual position of the leading part of the drummer, roller and disk in operation;

The impact wrench contains a housing consisting of two parts 1 and 2, spring-loaded between them. Engine part 3 is installed on part 2 of the case. In part 2, anvil 4 is placed with working cams 5 at one end and a turnkey head 6 at the other. The output shaft 7 of the engine 3 through the safety coupling to the coupling 8 is connected with a composite drummer installed in part 2 of the housing. The leading part 9 of the striker is made in the form of a glass with a central profile hole Yu passing into a circular hole 11, on the surface of which longitudinal profile grooves 12 are located. In the profile hole 10 of the driving part: 9 with the possibility of joint rotation and relative axial displacement intermediate ele

lateral surfaces of rollers 18. and their conical ends. Between the intermediate element 13 placed disk 22 with. radial points, the sides of which form an angle ct between them, the disk 22 is rigidly connected with the anvil 4 and functions as a device for controlling the impact geometry. Between the separator 16 and the part 1 of the striker there is a friction half coupling 25, which is spring-loaded relative to the disk 22 and mounted so that it can move relative to the roller 24, 4 or so.

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a gearing moment 13 having working cams 14 at one end and a conical surface 15 at the other end. In the hole 11 of the leading part Y, a separator 16 is installed with inclined radial grooves 17, which interact with the side surfaces of the rollers 18 with conical ends 19, which are placed in the profile grooves 12 of the leading part 9 and interact with the conical surface

15 intermediate element. 13 gearing.

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The separator 16 is installed in the leading part 9 with the possibility of rotation and from the side of the motor the wrench is made in the form of a conical friction half coupling 20 "

The intermeshing engagement element 13 is pressed from the anvil 14 by the spring 21 and has an external contour corresponding to the core 10 of the leading part 9 of the striker.

The impact geometry control device is made in the form of a disk 22 with radial notches 23 placed between the intermediate engagement element 13 and the separator 16 rigidly connected to the anvil 4 by means of a central roller 24 and oriented relative to the working cams 5 of the anvil. The response friction half coupling 20 separator

16 semi-coupling 25 is installed on the central roller 24 with the possibility of axial movement relative to ne3135

and through the thrust bearing 26 interacts with the leading part 9 of the striker, to which it is pressed by the spring 27. The lateral sides 28 of each of the profile grooves 12 form an angle / 3 between themselves, and the lateral sides 29 of the radial notches 23 of the disk 22 form an angle between themselves (L which is at least 10 more than the angle. The height of the working cams 5 of the anvil 4 is determined from the expression

H

- WG S -2ti 5

where H is the height of the working cams; Dp - diameter of the roller 18, mm; y is half the angle at the top of roller 18

Impact wrench works as follows.

The composite drummer receives rotation in one direction or another from the output shaft 7 of the engine 3. Together with the driving drum 9, the rollers 18, which are located in its profile grooves 12, and the separator 16, which are carried along by the rollers 18, rotate radial inclined grooves 17; When the rated speed is reached by the shaft 7 of the engine 3, i.e. after the striker has completed acceleration, the operator presses the engine handle (not shown) and, compressing the spring 27, moves the entire impact mechanism towards the anvil 4 relative to the body part 2. In this case, the coupling halves 20 and 25 of the friction clutch will first close, resulting in a sharp deceleration of the separator 16 with the rollers 18, as the coupling half 25 is rigidly connected with the anvil 4 through the central roller 24, which interacts with the adjustable key through the key 6 threaded connection (not shown). Further rotation of the leading part 9 of the firing pin causes the profile grooves 12 with the sides 28 to squeeze the rollers 18 towards the center of the firing pin. However, the movement of the rollers 18 is possible only in a strictly defined relative position of the leading part 9 of the striker and the anvil 4. Only at that point in time when the cams 14 of the intermediate element

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This 13 is located above the working cams 5 of the anvil 4, the rollers 18 begin to be squeezed out of the profile grooves 12 of the leading part 9 of the striker and crush into the radial notches 23 of the disk 22. Then as a result of the interaction of the conical ends 19 of the rollers 18 with the inclined grooves 17 of the separator 16 and the conical surface

15 intermediate element 13, the latter begins to move in the direction of the anvil 4. For a time less than the rotation time of the striker at an angle between the working cams 5 of the anvil 4, the intermediate element 13 moves axially to the full height of the engagement of its working cams 14, which are then applied to their side surfaces The impact on the response surfaces of the cams 5 of the anvil 4. In this case, the kinetic energy accumulated by the impactor is transferred to the threaded 5 threaded connection. Moreover, the rollers 18 have such a diameter and angles of the conic ends 19 that when axially moving the intermediate engagement element 13 into the engagement position with the cams 5 of the anvil 4, they move radially to the center of the impactor by a distance less than half the diameter of the rollers 18. Due to this upon impact, the rollers 18 are not completely out of their profile grooves 12.

The process of returning the rollers 18 is that by simultaneously acting on the rollers 18 of the lateral sides 28 of the profile groove 12 of the striker, the inclined surface 15 of the intermediate element 13, and the radial grooves 17 of the separator

16 and the lateral sides 29 of the radial insert 23 of the disk 22, the rollers 18 are able to immediately occupy their initial position in the drummer and exit from the radial notches 23 of the disk 22.

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FIG. 4 shows the position

the rollers 18 during their return to the initial position in the drummer at the worst possible position, when the rollers will be in contact with the side surfaces 28 and 29 of the groove 12 and the disk 22 as well. Atom, the rollers 18 are not stuck. since the angle formed between the side 28 of the groove 12 and.

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with the side 29 radially about the notch 23, there will always be a greater friction angle.

After the end of the strike process, the operator removes the force from the engine 3 handle. Then, under the action of the spring 27, the coupling half and 25 are released, and the separator 16 is able to rotate freely in the impactor. Return spring

21 intermediate element 13 through its conical surface 15 acts on the conical ends 19 of the rollers 18, while the rollers 18, interacting with the side surfaces

28 and 29 profile grooves 12 drummer and radial notches 23 of the disk

22, respectively, will be squeezed into the profile grooves 12 of the leading part 9 of the drummer. This is facilitated by the torque of the wrench motor,

as well as the angles og, and | b of the inclination of the lateral sides 28 and 29 of the profile grooves 12 and the radial notches 23, respectively, while the rollers 18 are not jammed during their return movement into the drummer.

After completion of the cam opening process, the entire cycle of operation of the impact wrench is repeated in this sequence.

Claims (1)

Invention Formula Impact wrench, comprising a housing, an engine mounted on it, placed in an anvil housing with working cams at one end and a turnkey head at the other, integral drummer, the leading part of which made in the form of a cup with longitudinal shaped grooves on the inner surface and connected to the engine output shaft, mounted in the leading part of the drummer with the possibility of joint rotation and relative axial movement and spring-loaded relative to the anvil intermediate member with counter cams at one end and a conical surface at the other end , a separator with radial inclined grooves, rollers with conical ends placed in the profile grooves to interact with the surfaces of inclined the grooves of the separator and the conical surface of the intermediate element and the impact geometry control device, made in the form of a radial blade disk rigidly connected to the anvil, and a friction clutch, characterized in that, in order to simplify the design of the wrench and increase reliability, the angle between the sides of each from radial cuts at least 10 ° more than the angle (5 formed by the sides of each of the profile grooves, and the height of the working anvil cams is determined from the expression H D - five, 2tgy where H is the height of the working anvil cams, Dp is the diameter of the roller, MMJ J is half the angle at the apex of the tapered end of the roller; 5 is a constant parameter. ;four h /four YU 29 27 srig.Z Jb 23 (puff.4