CN101092998A

CN101092998A - Heavy overrunning clutch

Info

Publication number: CN101092998A
Application number: CN 200710111387
Authority: CN
Inventors: 伍成林
Original assignee: Individual
Current assignee: Individual
Priority date: 2006-06-21
Filing date: 2007-06-19
Publication date: 2007-12-26

Abstract

This invention discloses a gravity-centrifugal force overriding clutch including a driving claw wheel, a driven ratch sleeve, in which a connection structure connected with a drive device is set on the driving claw wheel with claws, ratches are set on the internal circle wall of the driven ratch sleeve, the claws can be jointed with the ratches acted by gravity and centrifugal force and drawn back into the profile line of the driving claw wheel and installed on it breaking joint with the ratch on the driven ratch sleeve.

Description

Heavy-duty overrunning clutch

Technical Field

The invention provides an overrunning clutch used for a beam pumping unit.

Background

Spring-type overrunning clutches were used in beam-pumping units as early as 50 s in the united states, but because the pumping units were turned on and off once per stroke and 6-15 strokes per minute, the springs were damaged by fatigue in short periods of continuous operation. Therefore, the overrunning clutch cannot be widely used. In 2000, a magnet type overrunning clutch is used in a part of field tests in China, the service life of the magnet type overrunning clutch is greatly prolonged compared with a spring type clutch, but the magnetism of a magnet is gradually reduced along with the lapse of time, so that the overrunning clutch loses effect.

Disclosure of Invention

The invention aims to overcome the defects in the prior art and provide a heavy-clutch overrunning clutch which has long service life and reliable performance and realizes one-way power transmission by utilizing the combined action of gravity and centrifugal force.

The purpose of the invention is realized as follows:

the heavy-duty overrunning clutch provided by the invention comprises a driving pawl wheel and a driven ratchet sleeve, wherein a connecting structure connected with a driving device is arranged on the driving pawl wheel, a pawl piece is arranged on the driving pawl wheel, ratchets are arranged on the inner circumferential wall of the driven ratchet sleeve, the pawl piece can be jointed with the ratchets arranged on the inner circumferential wall of the driven ratchet sleeve under the action of gravity and centrifugal force, and the pawl piece can be retracted into the outer contour line of the driving pawl wheel and is installed on the driving pawl wheel in a way of being disengaged from the ratchets on the driven ratchet sleeve.

Specifically, there may be two preferred embodiments.

The first scheme is as follows: and a claw piece is connected to the circumference of the driving claw wheel in a manner of swinging around a hinge shaft through a hinge structure, and the claw piece on the driving claw wheel is matched with the ratchet on the inner wall of the driven ratchet sleeve.

The second scheme is as follows: the circumference of the driving pawl wheel is provided with a sliding structure which is a sliding channel arranged in the radial direction of the driving pawl wheel, a sliding pawl piece is arranged in the sliding channel, and the sliding pawl piece is matched with the ratchet on the inner wall of the driven ratchet sleeve.

The invention provides a heavy-clutch overrunning clutch, wherein shaft shoulders and hole shoulders which are matched with each other are further arranged on the side walls of a driving pawl wheel and a driven ratchet sleeve, ball grooves are arranged on the end surfaces of the shaft shoulders and/or the hole shoulders, and rolling bodies are arranged in the ball grooves.

Sealing covers are fixedly arranged on two end faces of the driven ratchet sleeve of the combined driving pawl wheel.

A gap is formed between the inner side surface of the sealing cover and the end surface of the driving claw wheel to ensure that the sealing cover and the driving claw wheel are not in contact with each other.

The corresponding shaft shoulder and hole shoulder are arranged on one adjacent end face of the driving claw wheel and the driven ratchet sleeve, the ball groove is arranged on the shaft shoulder and/or the hole shoulder between the driving claw wheel and the driven ratchet sleeve, the rolling body arranged in the ball groove is in contact with the end faces of the shaft shoulder and the hole shoulder, a bearing cover is fixedly connected to the other side of the driving claw wheel through a threaded connection structure, the ball groove is arranged on the bearing cover and the corresponding hole shoulder of the driven ratchet sleeve adjacent to the bearing cover, and the rolling body arranged in the ball groove is in contact with the end faces of the shoulder and the hole shoulder of the bearing cover.

The ball bearing is spaced from the ratchet teeth of the sawtooth-shaped step of the inner ring of the driven ratchet sleeve by a distance.

The heavy-clutch overrunning clutch provided by the invention realizes overrunning clutch between the driving pawl wheel and the driven ratchet sleeve through gravity and centrifugal force, has simple structure and reliable work, and particularly has longer service life than spring type and magnet type overrunning clutches in the prior art.

Drawings

The invention will be further explained with reference to the drawings.

FIG. 1 is a schematic cross-sectional view of a structural embodiment of a heavy-duty overrunning clutch provided in accordance with the present invention;

FIG. 2 is a side cross-sectional schematic view of the heavy duty overrunning clutch shown in FIG. 1;

FIG. 1a is a schematic cross-sectional view of another structural embodiment of a heavy duty overrunning clutch in accordance with the present invention;

FIG. 1c is a schematic diagram of an alternative arrangement of the jack block of FIG. 1a with springs;

FIG. 2a is a side cross-sectional schematic view of the heavy duty overrunning clutch shown in FIG. 1 a;

fig. 3 is a schematic structural diagram of a beam-pumping unit using the heavy-duty overrunning clutch.

Detailed Description

As shown in fig. 1 and 2, in an embodiment of the present invention, the heavy-duty overrunning clutch includes a driving dog wheel, also referred to as a driving dog wheel 3, and a driven ratchet sleeve, in this embodiment, the driven ratchet sleeve is a v-belt pulley 1, the driving dog wheel 3 is provided with a connection structure connected to the driving device, the connection structure is that a keyway shaft hole is formed in the center of the driving dog wheel 3, and an output shaft 0 of the driving device motor is fittingly arranged in the keyway shaft hole. The circumference of the driving pawl wheel 3 is connected with a pawl piece, also called a jack block 2, through a hinge structure, and can swing around a hinge shaft, the inner circumferential wall of the driven ratchet sleeve 1 is provided with a ratchet 4, the driving pawl wheel 3 is concentrically arranged in the cylinder body of the driven ratchet sleeve 1, and the pawl piece 2 on the driving pawl wheel 3 is matched with the ratchet 10 on the inner wall of the driven ratchet sleeve 1.

The jaw, also referred to herein as a jack block 2, is mounted on a drive jaw wheel, power wheel 3, the drive jaw wheel 3 in turn being connected to the output shaft 0 of the motor by a key 01. The operating principle of the heavy-duty overrunning clutch is as follows: when the motor does not rotate, the jack block 2 at the lower half part of the driving claw wheel 3 can be automatically opened under the action of self gravity to prop against the sawtooth step ratchet on the inner ring of the V-belt pulley 1. When the motor rotates, the jack can keep an open state due to the centrifugal force of the free end acting on the jack block 2 during high-speed rotation, and the unopened jack block is opened to prop against the ratchet 4 on the inner ring of the V-belt pulley 1, so that the purpose of transmitting power from the motor to the V-belt pulley is realized.

As shown in fig. 3, the heavy-duty overrunning clutch in this embodiment is applied to a driving pulley in a beam pumping unit in an oil field. When the pumping unit is in an up stroke, the triangular belt pulley 1 is reversely dragged by potential energy released by the rotating counterweight 17 in an accelerating way, so that the jack block 2 is automatically folded when the rotating speed exceeds the rotating speed of the motor, and the unidirectional transmission of power is realized.

The side walls of the driving claw wheel 3 and one side of the triangular belt pulley are also provided with a shaft shoulder 31 and a hole shoulder 12 which are matched with each other, the end surface of the hole shoulder 12 is provided with a ball groove, and a rolling body 6 is arranged in the ball groove. The outer end of the side is provided with a dust-proof sheet, i.e. a sealing cover 5, which is fixed on the side surface of the V-belt pulley 1 through screws, and a gap a is formed between the inner side surface of the sealing cover and the end surface of the driving pawl wheel 3. The other side wall of the driving claw wheel 3 is provided with a bearing cover 6, and the bearing cover 6 is fixedly connected with the driving claw wheel 3 through screw connection. A ball groove is provided between the bearing cap 6 and the adjacent bore shoulder of the v-belt pulley 1, in which the rolling bodies 6 are also provided. The dust-proof sheet 5 is provided on the outer surface of the bearing cover 6, and is fixed to the ground surface of the v-pulley 1 by screws in the same manner, with a gap from the end surface of the dog wheel 3.

Two sealing covers 5 are fixed on the end surfaces of the triangular belt wheel 1 through screws on the two end surfaces of the combined driving claw wheel and driven ratchet sleeve, and a central hole for enabling the output shaft of the motor to extend out is correspondingly arranged on each sealing cover 5.

The ball bearing 6 is provided to reduce frictional resistance when the dog wheel and the v-pulley move with each other.

The dustproof sheet 5 is arranged for preventing dust and rainwater from entering the inside of the clutch and ensuring the clutch to work normally for a long time.

The design must take into account:

1. the hinging shaft of the rotatable fixing end of the jack block 2 is reliably fixed, and the rotation friction is small, so that the jack block can be freely folded or unfolded under the action of gravity and centrifugal force.

The side surface of the power wheel 3 where the jack block 2 on the driving claw wheel 3 is located is provided with a groove 32, the shape and size of which are as follows: when the jack block 2 is folded, the jack block 2 is just in the contour line 33 of the power wheel and is abutted against the inner step 34 of the power wheel, and when the jack block 2 is unfolded, one side face 21 of the jack block 2 is abutted against the other side face 35 of the power wheel 3. The number of the jack blocks 2 and the length of the jack blocks 2 are preferably reduced on the premise that the jack blocks are reliably opened under the action of gravity and centrifugal force. The opening direction of the jack block is determined by the rotation direction of the motor of the field pumping unit.

2. The length of the sawtooth steps of the inner ring of the V-belt wheel 1 is required to be reduced on the premise that the jack block 2 can be opened in time.

3. The threaded connection between the bearing cap 8 and the power wheel 3 must be aligned and reliable. The outer end of the bearing cover 6 is properly provided with a punching pit so as to be convenient to detach and mount by utilizing a punch.

4. The dust-proof sheet 5 must ensure that dust rain cannot enter the inside of the overrunning clutch. The belt wheel is connected to the triangular belt wheel 1 by screws and is not contacted with the power wheel 3 so as to ensure that the power wheel 3 is not rubbed.

5. The

ball bearings

6, 9 are spaced from the saw-tooth step of the inner ring of the v-belt pulley by a suitable distance to prevent grease from sticking to the jack block 2.

6. The main stressed components have to meet the strength requirement during working, and the safety coefficient is properly increased.

As shown in fig. 1a and 2a, in another embodiment of the present invention, the heavy-duty overrunning clutch also includes a driving dog wheel, also referred to as a power wheel 3, and a driven ratchet sleeve, in this embodiment, the driven ratchet sleeve is a v-belt pulley 1, the power wheel 3 is provided with a connection structure connected with the driving device, the connection structure is that a keyway shaft hole is formed in the center of the driving dog wheel 3, and an output shaft 0 of the driving device motor is fittingly arranged in the keyway shaft hole. The circumference of the driving pawl wheel 3 is provided with a sliding structure which is a sliding channel 11 arranged in the radial direction of the driving pawl wheel, a sliding pawl piece 2 is arranged in the sliding channel, the sliding channel 11 is internally provided with the sliding pawl piece which is also called a jack block 2 through the sliding structure, the inner circumferential wall of the driven ratchet sleeve 1 is provided with a ratchet 4, the driving pawl wheel 3 is concentrically arranged in the cylinder body of the driven ratchet sleeve 1, and the pawl piece 2 on the driving pawl wheel 3 is matched with the ratchet 4 on the inner wall of the driven ratchet sleeve 1.

The jaw, also referred to herein as a jack block 2, is mounted in a slideway on a driving jaw wheel, i.e. a power wheel 3, which power wheel 3 is in turn connected to the output shaft 0 of the motor by means of a key 01. The operating principle of the heavy-duty overrunning clutch is as follows: when the motor does not rotate, the jack block 2 positioned on the lower half part of the power wheel 3 can automatically slide out along the slide way under the action of self gravity to prop against the sawtooth step-shaped ratchet on the inner ring of the V-belt pulley 1. When the motor rotates, the jack can keep the state of propping the sawtooth step-shaped ratchets on the inner ring of the V-belt pulley 1 due to the centrifugal force acting on the jack block 2 during high-speed rotation, and the jack block which does not slide out of the slideway is opened to prop the ratchets 4 on the inner ring of the V-belt pulley 1, so that the purpose of transmitting power to the V-belt pulley from the motor is realized.

As shown in fig. 3, the heavy-duty overrunning clutch in this embodiment is applied to the driving pulley of the beam-pumping unit in the oil field, which is the same as that in embodiment 1. When the pumping unit is in the up stroke, the potential energy released by the rotating balance weight 17 in an accelerating way reversely drags the V-belt pulley 1, so that the rotating speed of the V-belt pulley exceeds the rotating speed of the motor, the jack block 2 automatically retracts into the sliding way and is folded, and the unidirectional transmission of power is realized.

The side wall of one side of the power wheel 3 and the triangular belt pulley 1 is also provided with a shaft shoulder 5 and a hole shoulder 16 which are matched with each other, the end surface of the hole shoulder 16 is provided with a ball groove, and a rolling body 6 is arranged in the ball groove. The outer end of the side is provided with a dust-proof sheet, i.e. a sealing cover 7, which is fixed on the side surface of the V-belt pulley 1 through screws, and a gap a is formed between the inner side surface of the sealing cover and the end surface of the power wheel 3. And a bearing cover 8 is arranged on the other side wall of the power wheel 3, and the bearing cover 8 is fixedly connected with the power wheel 3 through a bolt. A ball groove is provided between the bearing cap 8 and the adjacent bore shoulder of the v-belt pulley 1, in which also rolling bodies 9 are provided. The dust-proof sheet 10 is fixed to the side surface of the v-pulley 1 by a screw, and a gap a is provided between the dust-proof sheet and the end surface of the power wheel 3.

Two sealing covers 7 and 10 are fixed on the end surfaces of the triangular belt wheel 1 through screws on the two end surfaces of the combined driving pawl wheel and driven ratchet sleeve, and a central hole for enabling the output shaft of the motor to extend out is correspondingly arranged on the sealing covers 7 and 10.

The

ball bearings

6 and 9 are provided to reduce frictional resistance when the power wheel and the v-pulley move with each other.

The

dustproof sheets

7 and 10 are arranged for preventing dust and rainwater from entering the inside of the clutch and ensuring the clutch to work normally for a long time.

The design must take into account:

1. the jack block 2 can be slidably arranged in the sliding channel, and meanwhile, the sliding friction is small, so that the jack block can freely slide into or slide out of the sliding channel under the action of gravity and centrifugal force.

The sliding channel 11 arranged on the power wheel 3 at the position of the jack block 2 on the power wheel 3 has the shape and size as follows: when the jack block 2 slides into the slideway, the jack block 2 is just right in the contour line 12 of the power wheel and abuts against the inner step 13 of the slideway on the power wheel, and when the front part of the jack block 2 slides out of the slideway, the side surface 14 of the rear part of the jack block 2 abuts against the side surface 15 of the slideway on the power wheel 3, namely the jack block 2 can not completely separate from the slideway. The number of the jack blocks 2 and the length of the jack blocks 2 are required to ensure that the clutch can safely work normally without being damaged when any one jack block works alone on the premise that the jack blocks are reliably opened under the action of gravity and centrifugal force. The stress surface of the jack block is determined by the rotation direction of the motor of the field oil pumping unit.

3. The threaded connection between the bearing cap 8 and the power wheel 3 must be aligned and reliable. The outer end of the bearing cover 8 is properly provided with a punching pit so as to be convenient to detach and mount by utilizing a punch.

4. The dust flaps 7, 10 must ensure that dust rain cannot enter the inside of the overrunning clutch. The belt wheel is connected to the triangular belt wheel 1 by screws and is not contacted with the power wheel 3 so as to ensure that the power wheel 3 is not rubbed.

5. The

ball bearings

6, 9 are spaced from the saw-tooth step of the inner ring of the v-belt pulley by a suitable distance to prevent grease from entering the slide way of the jack block 2.

7. In case of low motor speed or high friction, a spring 18 may be added between the jack block 2 and the sliding channel 11, as shown in fig. 1c, to allow the jack block to be opened instantly.

The heavy-clutch overrunning clutch provided by the invention can also be used for clutch connection between a driving part and a driven part which need to have different rotating speeds and have various structures relatively.

When the heavy-clutch overrunning clutch jack block moves circularly under the action of the motor, the stress on the jack block is analyzed as follows:

as shown in fig. 1, when the jack block moves to the highest point of the circumference, the force acting on the jack block at this time has its own gravity in a vertically downward direction and also has a centrifugal force in a vertically upward direction. It is known that gravity is at this point a negative factor preventing the jack blocks from opening, and that the centrifugal force acting on the jack blocks at any position of the circumference is always directed straight outwards, and therefore always powers the opening of the jack blocks.

By derivation, it can be found that the ratio of the centrifugal force to the gravity acting on the jack block is:

by analyzing the above formula, it can be known that: the force ratio is proportional to the radius of the circular motion of the jack block and proportional to the square of the motor speed. The greater the force ratio, the greater the power to open the jack block.

Looking up the technical specifications of motors in the fourth sublist table 1-18 of the oil extraction technical manual, wherein the rotating speed of the motor used by each type of pumping unit is in the range of 490-1400 rpm; looking up the manual table 1-14 technical specifications of the floating beam type pumping unit, the diameter of the motor pulley of each type of pumping unit is within the range of 102-. Taking the parameters which are most unfavorable for opening the jack block to calculate the force ratio, and taking the motor with the lowest rotating speed, namely the rotating speed of the motor is 490 r/min; the diameter of the smallest motor belt pulley is equal to 102 mm, occupied parts such as a triangular belt and the like are removed, and the circular motion radius of the jack block is 0.033 m.

Substituting the parameters most unfavorable for opening the jack block into the formula to obtain:

the calculation is a force ratio calculation based on the parameters of all pumping units in the whole body which are most unfavorable to the opening of the jack block, and the force for opening the jack block is enough when the heavy-clutch overrunning clutch works under the most unfavorable force ratio (namely 8.54 times). And it is known that the force for opening the jack block is not changed along with the increase of the working time of the oil pumping unit, while the force for opening the jack block of the spring type overrunning clutch and the magnetic type overrunning clutch is gradually reduced along with the increase of the working time, and finally the working capacity is lost. Therefore, the advantages of the heavy-duty overrunning clutch provided by the invention compared with the prior art can be further proved.

Claims

1. A heavy duty overrunning clutch, comprising: the ratchet wheel comprises a driving pawl wheel and a driven ratchet sleeve, wherein a connecting structure connected with a driving device is arranged on the driving pawl wheel, pawl members are arranged on the driving pawl wheel, ratchets are arranged on the inner circumferential wall of the driven ratchet sleeve, the pawl members can be jointed with the ratchets arranged on the inner circumferential wall of the driven ratchet sleeve under the action of gravity and centrifugal force, and can be retracted into the outer contour line of the driving pawl wheel to be separated from the ratchets on the driven ratchet sleeve and are arranged on the driving pawl wheel.

2. The heavy duty overrunning clutch according to claim 1, wherein: and a claw piece is connected to the circumference of the driving claw wheel in a manner of swinging around a hinge shaft through a hinge structure, and the claw piece on the driving claw wheel is matched with the ratchet on the inner wall of the driven ratchet sleeve.

3. The heavy duty overrunning clutch according to claim 1, wherein: the circumference of the driving claw wheel is provided with a sliding structure which is a sliding channel arranged in the radial direction of the driving claw wheel, a sliding claw piece is arranged in the sliding channel, and the sliding claw piece is matched with the ratchet on the inner wall of the driven ratchet sleeve.

4. The heavy duty overrunning clutch according to claim 2, wherein: the side surface of the driving claw wheel at the position of the claw piece on the driving claw wheel is provided with a groove, and the shape and the size of the groove are as follows: when the claw piece is folded, the claw piece is just positioned in the contour line of the driving claw wheel and abuts against the inner step of the driving claw wheel, and when the claw piece is unfolded, one side surface of the claw piece abuts against one side surface of the driving claw wheel.

5. The heavy duty overrunning clutch according to claim 3, wherein: the shape and size of the sliding channel arranged on the driving claw wheel where the claw piece on the driving claw wheel, namely the jack block, is as follows: when the front part of the jack block slides out of the slide way to be engaged with the ratchet teeth arranged on the inner circumferential wall of the driven ratchet sleeve, the side surface of the rear part of the jack block abuts against the side surface of the slide way on the driving pawl wheel, namely the jack block cannot completely fall out of the slide way; or,

the shape and size of the sliding channel arranged on the driving claw wheel where the claw piece on the driving claw wheel, namely the jack block, is as follows: when the front part of the jack block slides out of the slide way to be engaged with the ratchet teeth arranged on the inner circumferential wall of the driven ratchet sleeve, the side surface of the rear part of the jack block abuts against the side surface of the slide way on the driving pawl wheel, namely the jack block cannot completely fall out of the slide way; and a spring is additionally arranged between the jack block and the sliding channel.

6. The heavy duty overrunning clutch according to any one of claims 1 to 4, wherein: the side walls of the driving claw wheel and the driven ratchet sleeve are also provided with a shaft shoulder and a hole shoulder which are matched with each other, the end surface of the shaft shoulder and/or the hole shoulder is provided with a ball groove, and a rolling body is arranged in the ball groove.

7. The heavy duty overrunning clutch according to any one of claims 1 to 4, wherein: and sealing covers are arranged on two end surfaces of the combined driving pawl wheel and driven ratchet sleeve.

8. The heavy duty overrunning clutch according to claim 7, wherein: a gap is formed between the inner side surface of the sealing cover and the end surface of the driving claw wheel to ensure that the sealing cover and the driving claw wheel are not in contact with each other.

9. The heavy duty overrunning clutch according to claim 7 or 8, wherein: the corresponding shaft shoulder and hole shoulder are arranged on one adjacent end face of the driving claw wheel and the driven ratchet sleeve, the ball groove is arranged on the shaft shoulder and/or the hole shoulder between the driving claw wheel and the driven ratchet sleeve, the rolling body arranged in the ball groove is in contact with the end faces of the shaft shoulder and the hole shoulder, a bearing cover is fixedly connected to the other side of the driving claw wheel through a threaded connection structure, the ball groove is arranged on the bearing cover and the corresponding hole shoulder of the driven ratchet sleeve adjacent to the bearing cover, and the rolling body arranged in the ball groove is in contact with the end faces of the shoulder and the hole shoulder of the bearing cover.

10. The heavy duty overrunning clutch according to claim 9, wherein: and a distance is reserved between the ball bearing and the ratchet of the sawtooth-shaped step of the inner ring of the driven ratchet sleeve.