A cylinder arm pin drive mechanism and a single-cylinder pin telescopic system

Abstract

This invention discloses a cylinder boom pin drive mechanism, comprising: a first cylinder head body at one end of the telescopic cylinder barrel near the tail of the boom, and a second cylinder head body at the other end of the telescopic cylinder barrel away from the tail of the boom; the first cylinder head body has a first cylinder head body dovetail groove and a first cylinder head body pin; the second cylinder head body has a second cylinder head body dovetail groove and a second cylinder head body pin; the drive cylinder is a double-acting double-piston rod cylinder, wherein when piston rod one extends, it drives the first cylinder head body pin and the second cylinder head body pin to move synchronously, and when piston rod one retracts, the first cylinder head body pin and the second cylinder head body pin are reset by a return spring; when piston rod two extends, it drives the first cylinder head body dovetail groove and the second cylinder head body dovetail groove to move synchronously, and when piston rod two retracts, the first cylinder head body dovetail groove and the second cylinder head body dovetail groove are reset by a return spring.

Description

Technical Field

[0001] This invention relates to a cylinder arm pin drive mechanism and a single-cylinder pin telescopic system, belonging to the field of crane technology. Background Technology

[0002] Single-cylinder pin-type lifting jib has typical characteristics such as no limitation on jib length, smooth jib cross-section change, and high lifting capacity, and is widely used in the crane industry.

[0003] Traditional single-cylinder pin-type telescopic mechanisms use a single cylinder head mounted on a telescopic cylinder to achieve the telescopic boom's extension and retraction. The stroke of this type of cylinder exceeds the maximum stroke of each boom section. To ensure such a large stroke and stable extension of the boom, the cylinder rod and barrel need to be very thick and long, requiring a larger oil tank to supply more hydraulic fluid. This results in high cylinder costs and excessive weight on the crane.

[0004] Later improvements addressed the shortcomings of single-cylinder telescopic mechanisms, resulting in a double-cylinder telescopic mechanism. This involves mounting two cylinder heads, one in front of the other, on the telescopic cylinder, using a relay-force method to extend and retract the crane boom. This shortens the cylinder length, reduces the cylinder diameter and rod diameter, lowers cylinder costs, and simultaneously reduces the size of the oil tank, decreasing the weight on the crane and increasing lifting capacity, thus allowing for greater design flexibility in crane design.

[0005] In the existing technical solution, the actuation mechanisms of the two cylinder heads are completely independent, with synchronization of movement only ensured by a common hydraulic oil source. The movement of the cylinder pins and dovetail grooves of the two cylinder heads requires two sets of drive elements, and sensors need to be installed separately to detect their respective positions.

[0006] The existing telescopic system technical solution requires the synchronous movement of the cylinder pins of the two cylinder heads and the synchronous movement of the dovetail grooves of the two cylinder heads. However, the action mechanisms of the two cylinder heads are independent and can only be synchronized by the hydraulic system, that is, to synchronously supply pressurized oil to the two cylinder pin drive cylinders or dovetail groove drive cylinders.

[0007] In existing twin-cylinder head designs, the front and rear cylinder heads operate independently, sharing a common hydraulic power source for synchronized movement. This design relies on two detection switches for the cylinder arm pin position detection of each cylinder head, requiring a total of eight switches across both cylinder heads. In practical applications, the large number of switches, coupled with the inherent reliability limitations of individual detection units, leads to low overall reliability of the telescopic system. The twin-cylinder head arrangement necessitates placing one cylinder head at the front of the hydraulic cylinder, away from the boom tail, resulting in extremely poor maintainability. Furthermore, the two cylinder heads require two sets of drive components and two sets of position detection components, increasing cost and reducing reliability compared to a single-cylinder head design. Summary of the Invention

[0008] The purpose of this invention is to provide a cylinder arm pin drive mechanism and a single-cylinder pin telescopic system to solve the defects of poor reliability and high cost caused by too many components in the prior art.

[0009] A cylinder arm pin drive mechanism, comprising:

[0010] The telescopic cylinder barrel has a first cylinder head body at one end near the tail of the boom, and a second cylinder head body at the other end away from the tail of the boom.

[0011] The first cylinder head body is provided with a first cylinder head body dovetail groove and a first cylinder head body pin; the second cylinder head body is provided with a second cylinder head body dovetail groove and a second cylinder head body pin.

[0012] A driving cylinder, wherein the driving cylinder is a double-acting double-piston rod cylinder, including an A oil chamber and a B oil chamber, wherein a piston rod one is provided in the A oil chamber and a piston rod two is provided in the B oil chamber;

[0013] When the piston rod extends, it drives the first cylinder head body pin and the second cylinder head body pin to move synchronously. When the piston rod retracts, the first cylinder head body pin and the second cylinder head body pin are reset by the return spring.

[0014] The piston rod extends and drives the first cylinder head dovetail groove and the second cylinder head dovetail groove to move synchronously. When the piston rod retracts, the first cylinder head dovetail groove and the second cylinder head dovetail groove are reset by the reset spring.

[0015] Furthermore, the piston rod abuts against a pressure rod, the pressure rod is connected to a partition b, and communicates with the first cylinder head pin; the second cylinder head pin is connected to the partition b through a connecting plate b and a long pull rod.

[0016] Furthermore, the piston rod 2 abuts against the connecting plate a, the first cylinder head body dovetail groove is connected to the connecting plate a through pull rod a and pull rod b, the pull rod a and pull rod b are connected to a partition plate a at one end near the first cylinder head body dovetail groove, and the second cylinder head body dovetail groove is connected to the connecting plate a through a long pressure rod.

[0017] Furthermore, the reset spring is disposed between partition a and partition b.

[0018] Furthermore, detection switches are provided at the starting and target positions of the movement of partition a and partition b to detect the positions of partition a and partition b.

[0019] Furthermore, the long tie rod includes a long tie rod a and a long tie rod b, with the long tie rod a located between the top of the connecting plate b and the partition plate b, and the long tie rod b located between the bottom of the connecting plate b and the partition plate b.

[0020] Furthermore, the long pressure rod includes a long pressure rod a and a long pressure rod b. The long pressure rod a is located between the dovetail groove of the second cylinder head body and the top of the connecting plate a, and the long pressure rod b is located between the dovetail groove of the second cylinder head body and the bottom of the connecting plate a.

[0021] A single-cylinder pin telescopic system includes the cylinder arm pin drive mechanism described in any of the above claims.

[0022] Compared with the prior art, the beneficial effects achieved by the present invention are as follows:

[0023] The present invention provides the following advantages by rigidly connecting the front and rear cylinder head moving mechanisms:

[0024] 1) Replacing hydraulic linkage with more reliable mechanical linkage enables strict synchronization of the movement of the cylinder head and cylinder arm pins, reducing the number of hydraulic drive units from two to one, thus significantly improving the reliability of the drive system. Simultaneously, halving the number of drive units will optimize hydraulic piping, reducing the number and length of pipes and lowering hydraulic costs.

[0025] 2) The number of cylinder arm pin position detection switches on the cylinder head body has been reduced from 8 to 4. Since the failure rate of position detection switches on the market is relatively high, the reliability of the electrical system can be greatly improved, while reducing the cost of electrical testing.

[0026] 3) Due to the influence of the boom structure, the cylinder head body far from the tail of the boom has extremely poor maintainability. Eliminating the detection switch, drive cylinder and other components of this cylinder head body can greatly improve the maintainability of the telescopic system. Attached Figure Description

[0027] Figure 1 This is a mechanical linkage diagram of the double cylinder head body of the present invention;

[0028] In the diagram: 1-First cylinder head body; 2-Dovetail groove of first cylinder head body; 3-Cylinder pin of first cylinder head body; 4-Baffle a; 5-Reset spring; 6-Baffle b; 7-Drive cylinder; 8-Piston rod one; 9-Piston rod two; 10.1-Tie rod a; 10.2-Tie rod b; 11-Connecting plate a; 12-Cylinder barrel of telescopic cylinder; 13-Connecting plate b; 14-Pressure rod; 15.1-Long pressure rod a; 15.2-Long pressure rod b; 16.1-Long tie rod a; 16.2-Long pressure rod b; 17-Cylinder pin of second cylinder head body; 18-Dovetail groove of second cylinder head body; 19-Second cylinder head body. Detailed Implementation

[0029] To make the technical means, creative features, objectives and effects of this invention easier to understand, the invention will be further described below in conjunction with specific embodiments.

[0030] like Figure 1 As shown, a cylinder head pin drive mechanism is disclosed, which rigidly connects the front and rear cylinder heads together via a connecting rod. The movement of the cylinder pins and dovetail grooves of the front and rear cylinder heads is changed from hydraulic linkage to more reliable mechanical linkage. Therefore, one set of drive elements and position detection elements for the movement of the cylinder pins and dovetail grooves can be reduced, solving the problems of poor reliability and high cost caused by too many elements. At the same time, the drive elements and position detection elements are arranged in the cylinder head near the tail of the boom, solving the problem of poor maintainability of the cylinder head far from the tail of the boom. The specific structure includes:

[0031] The telescopic cylinder barrel 12 has a first cylinder head body 1 at one end near the tail of the boom and a second cylinder head body 19 at the other end away from the tail of the boom.

[0032] The first cylinder head body 1 is provided with a first cylinder head body dovetail groove 2 and a first cylinder head body cylinder pin 3; the second cylinder head body 19 is provided with a second cylinder head body dovetail groove 18 and a second cylinder head body cylinder pin 17.

[0033] The driving cylinder 7 is a double-acting double-piston rod cylinder, including an oil chamber A and an oil chamber B. The oil chamber A is provided with a piston rod 8 and the oil chamber B is provided with a piston rod 9.

[0034] The piston rod 8 extends and drives the first cylinder head pin 3 and the second cylinder head pin 17 to move synchronously. When the piston rod 8 retracts, the first cylinder head pin 3 and the second cylinder head pin 17 are reset by the return spring 5.

[0035] The piston rod 29 extends and drives the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18 to move synchronously. When the piston rod 29 retracts, the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18 are reset by the return spring 5.

[0036] In this embodiment, the structure is further described in detail. The piston rod 8 abuts against the pressure rod 14. Here, the abutment is a separate connection, meaning that when the piston rod 8 moves to the left from its initial position, it can push the pressure rod 14 to move synchronously to the left; when the piston rod 8 moves to the right from its initial position, it disengages from the pressure rod 14. The pressure rod 14 is connected to a partition plate b6 and communicates with the first cylinder head pin 3. The second cylinder head pin 17 is connected to the partition plate b6 through a connecting plate b13 and a long pull rod. The pressure rod 14 is simultaneously connected to the partition plate 6 and moves synchronously through the connecting plate b13 and the long pull rod, causing the first cylinder head pin 3 and the second cylinder head pin 17 to move synchronously.

[0037] In this embodiment, the structure is further described in detail. The piston rod 9 abuts against the connecting plate a11. This abutment is also a separate connection, that is, when the piston rod 9 moves to the right from its initial position, it can push the connecting plate a11 to move synchronously to the right. When the piston rod 9 moves to the left from its initial position, it disengages from the connecting plate a11. The first cylinder head dovetail groove 2 is connected to the connecting plate a11 through the pull rods a10.1 and b10.2. The pull rods a10.1 and b10.2 are connected to a partition plate a4 at the end near the first cylinder head dovetail groove 2. The second cylinder head dovetail groove 18 is connected to the connecting plate a11 through a long pressure rod. Specifically, the first cylinder head dovetail groove 2 is connected to the connecting plate a11 through the pull rod, and the second cylinder head dovetail groove 18 is connected to the connecting plate a11 through the long pressure rod, thereby realizing the synchronous movement of the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18.

[0038] In the above scheme, piston rod 8 is separately connected to pressure rod 14, and piston rod 9 is separately connected to connecting plate a11. When piston rod 8 and piston rod 9 retract, they cannot drive the first cylinder head pin 3 and the second cylinder head pin 17, the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18 to retract. Therefore, a return spring 5 is set between partition a4 and partition b6. The purpose of this setting is to solve the problem of too many components. Only detection switches need to be set at the starting position and target position of the movement of partition a4 and partition b6 to detect the position of partition a4 and partition b6. Detection switches are arranged at the starting position and target position of the movement of partitions 4 and 6 to detect the position of the partitions, which can detect the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18, the first cylinder head pin 3 and the second cylinder head pin 17. Therefore, a total of 4 detection switches are needed. Figure 1 S1 to S4 are shown in the diagram.

[0039] In this embodiment, the long tie rod includes a long tie rod a16.1 and a long tie rod b16.2. The long tie rod a16.1 is located between the top of the connecting plate b13 and the partition plate b6, and the long tie rod b16.2 is located between the bottom of the connecting plate b13 and the partition plate b6. The arrangement of the two rods ensures the stability of the movement.

[0040] In this embodiment, the long pressure rod includes a long pressure rod a15.1 and a long pressure rod b15.2. The long pressure rod a15.1 is located between the dovetail groove 18 of the second cylinder head body and the top of the connecting plate a11, and the long pressure rod b15.2 is located between the dovetail groove 18 of the second cylinder head body and the bottom of the connecting plate a11. The arrangement of the two rods can ensure the stability of the movement.

[0041] The main working principle of this invention:

[0042] Cylinder pin retraction: High-pressure oil is supplied to port B of the drive cylinder 7, and oil is returned from port A. The piston rod 8 extends to the left, pushing the pressure rod 14 and the partition b6 to move to the left.

[0043] The first cylinder head pin 3 retracts inward under the action of the pressure rod 14. The long pull rods a16.1 and b16.2, and the connecting plate b13 move to the left under the pull of the connecting plate 6, thereby pulling the second cylinder head pin 17 inward. Simultaneously, the return spring 5 is compressed and stores force under the action of the partition b6. At this time, the piston rod 9 disengages from the connecting plate a11, and the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18 remain stationary.

[0044] Cylinder pin release: Oil ports B and A of the drive cylinder 7 are both connected to the oil return pressure relief system. Under the action of the return spring 5, the partition b6 moves to the right. The partition b6 pulls the pressure rod 14 to the right, which in turn pulls the first cylinder head cylinder pin 3 outward for release.

[0045] Long tie rods a16.1 and b16.2, along with connecting plate b13, move synchronously to the right under the action of partition b6, thereby enabling the second cylinder head pin 17 to be released outwards synchronously. Simultaneously, piston rod 8 moves to the right to its initial position under the push of pressure rod 14.

[0046] Dovetail groove pull-down: High-pressure oil is supplied to port A of the drive cylinder 7, and oil returns from port B. Piston rod 9 extends to the right, pushing connecting plate a11 to move to the right. Connecting plate a11 drives pull rods a10.1, b10.2, long pressure rods a15.1 and b15.2 to move to the right, thereby realizing the synchronous downward movement of the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18. At the same time, the return spring 5 is compressed and stored under the action of partition a4. At this time, piston rod 8 disengages from partition b6, and the first cylinder head pin 3 and the second cylinder head pin 17 do not move.

[0047] Dovetail groove release: Oil ports B and A of the drive cylinder 7 are both connected to the oil return pressure relief system. Under the action of the return spring 5, the partition a4 moves to the left. The partition a4 pulls the pull rods a10.1, b10.2, a15.1, and b15.2 to the left, thereby realizing the synchronous upward release of the first cylinder head dovetail groove 2 and the second cylinder head dovetail groove 18. At the same time, the piston rod 9 moves to the left to its initial position under the push of the connecting plate a11.

[0048] The present invention also discloses a single-cylinder pin telescopic system, including the cylinder arm pin drive mechanism described above.

[0049] The above description is only a preferred embodiment of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the scope of protection of the present invention.

Claims

1. A cylinder arm pin drive mechanism, characterized in that, include: The telescopic cylinder barrel (12) has a first cylinder head body (1) at one end near the tail of the boom and a second cylinder head body (19) at the other end away from the tail of the boom. The first cylinder head body (1) is provided with a first cylinder head body dovetail groove (2) and a first cylinder head body cylinder pin (3); the second cylinder head body (19) is provided with a second cylinder head body dovetail groove (18) and a second cylinder head body cylinder pin (17). The driving cylinder (7) is a double-acting double piston rod cylinder, including an A oil chamber and a B oil chamber. The A oil chamber is provided with a piston rod one (8), and the B oil chamber is provided with a piston rod two (9). The piston rod (8) extends and drives the first cylinder head pin (3) and the second cylinder head pin (17) to move synchronously. When the piston rod (8) retracts, the first cylinder head pin (3) and the second cylinder head pin (17) are reset by the return spring (5). The piston rod 2 (9) extends and drives the first cylinder head dovetail groove (2) and the second cylinder head dovetail groove (18) to move synchronously. When the piston rod 2 (9) retracts, the first cylinder head dovetail groove (2) and the second cylinder head dovetail groove (18) are reset by the reset spring (5). The piston rod (8) abuts against the pressure rod (14), the pressure rod (14) is connected to the partition plate b (6) and communicates with the first cylinder head body pin (3); the second cylinder head body pin (17) is connected to the partition plate b (6) through the connecting plate b (13) and the long pull rod; The piston rod 2 (9) abuts against the connecting plate a (11). The first cylinder head dovetail groove (2) is connected to the connecting plate a (11) through the pull rod a (10.1) and the pull rod b (10.2). The pull rod a (10.1) and the pull rod b (10.2) are connected to the partition plate a (4) at one end near the first cylinder head dovetail groove (2). The second cylinder head dovetail groove (18) is connected to the connecting plate a (11) through the long pressure rod. The reset spring (5) is located between the partition plate a (4) and the partition plate b (6).

2. The cylinder arm pin drive mechanism according to claim 1, characterized in that, The starting and target positions of the movement of the partition a (4) and partition b (6) are set with detection switches to detect the positions of the partition a (4) and partition b (6).

3. The cylinder arm pin drive mechanism according to claim 1, characterized in that, The long tie rod includes a long tie rod a (16.1) and a long tie rod b (16.2). The long tie rod a (16.1) is located between the top of the connecting plate b (13) and the partition b (6), and the long tie rod b (16.2) is located between the bottom of the connecting plate b (13) and the partition b (6).

4. The cylinder arm pin drive mechanism according to claim 1, characterized in that, The long pressure rod includes a long pressure rod a (15.1) and a long pressure rod b (15.2). The long pressure rod a (15.1) is located between the dovetail groove (18) of the second cylinder head body and the top of the connecting plate a (11), and the long pressure rod b (15.2) is located between the dovetail groove (18) of the second cylinder head body and the bottom of the connecting plate a (11).

5. A single-cylinder pin telescopic system, characterized in that, Includes the cylinder arm pin drive mechanism as described in any one of claims 1-4.

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