CN111761852B - Novel lightweight complete dynamic balance mode and device for double-shaft four-point high-speed press - Google Patents
Novel lightweight complete dynamic balance mode and device for double-shaft four-point high-speed press Download PDFInfo
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- CN111761852B CN111761852B CN202010513186.6A CN202010513186A CN111761852B CN 111761852 B CN111761852 B CN 111761852B CN 202010513186 A CN202010513186 A CN 202010513186A CN 111761852 B CN111761852 B CN 111761852B
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/26—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by cams, eccentrics, or cranks
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
Abstract
The invention relates to a new light-weight complete dynamic balance mode and a device thereof for a double-shaft four-point high-speed press, which comprise a frame, a movable cross beam, a double-shaft four-point crank slider mechanism, an auxiliary connecting rod, an auxiliary slider, a balancing weight and an eccentric gear set, wherein the movable cross beam is arranged on the frame; the movable cross beam is arranged on the frame and can move up and down along the guide rail of the frame to adjust the die filling height, and the crankshaft of the double-shaft four-point crank slide block actuating mechanism is arranged on the movable cross beam through a bearing seat; the auxiliary connecting rod, the auxiliary sliding block and the crankshaft also form a crank sliding block mechanism, and the balancing weight is fixedly connected with the crankshaft and rotates at the same angular speed when the crankshaft works; the large gear of the eccentric gear set is fixed to the crankshaft and rotates at the same angular velocity while meshing with the eccentric small gear when the crankshaft operates. The invention can realize good dynamic balance effect of the high-speed press by using smaller mass, and when the mass of the sliding block and the upper die is changed, the mass of the balancing weight and the eccentric pinion can be steplessly adjusted, thereby ensuring good dynamic balance effect.
Description
Technical Field
The invention belongs to the technical field of high-speed presses, and particularly relates to a novel lightweight complete dynamic balance mode and device for a double-shaft four-point high-speed press.
Background
The high-speed press is widely applied to industrial production because of the advantages of automation, high efficiency and precision. The stroke times per minute of the slide block of the general mechanical press is generally not more than 200rpm, while the stroke times per minute of the slide block of the high-speed press is much higher than that of the general mechanical press, and some of the stroke times per minute of the slide block of the high-speed press are even more than 1000rpm, at the moment, the unbalance phenomenon in the operation of the high-speed press is obviously increased, the vibration of a machine tool caused by the unbalance is more severe, the service life of a die is seriously influenced, and the processing precision of parts is greatly reduced.
The current common dynamic balance structure of the high-speed press is that a counterweight block opposite to the eccentricity of a crankshaft is assembled on the crankshaft, or a mode of symmetrically and reversely arranging crank blocks is adopted for balancing the inertia force of the crank block mechanism during high-speed operation.
However, the dynamic balance mode of the existing high-speed press still has some problems to be solved:
(1) the crankshaft is provided with the rotating eccentric balancing weight which can only balance the first-order inertia force of the sliding block of the high-speed press and can not balance the inertia force of the connecting rod and the second-order and high-order inertia forces of the sliding block, so that only partial balance can be realized, and the balance effect is poor;
(2) although the balance mode of the symmetrical inverted crank connecting rod sliding block can realize thorough balance of inertia force, the mass of the auxiliary sliding block of the balance mode is large, so that the weight of a machine is increased, the installation and debugging are inconvenient, the manufacturing and processing cost is high, the dynamic response of a press is slow, and the energy consumption is increased.
(3) Whether a rotating eccentric counterweight block structure or a symmetrical inverted crank sliding block structure is arranged on a crankshaft, when the mass of the sliding block and the upper die changes, the mass of the counterweight block or the inverted auxiliary sliding block is difficult to adjust, so that the dynamic balance effect is reduced sharply;
therefore, it is necessary to design a low-mass balance mechanism capable of achieving good dynamic balance of the high-speed press.
Disclosure of Invention
In order to solve the problems in the prior art, the invention provides a novel lightweight complete dynamic balance mode and a device thereof for a double-shaft four-point high-speed press, which can realize good balance of the inertia force of the press and have low mass at the same time, and when the mass of a slide block and the mass of an upper die are changed, a dynamic balance mechanism can be adjusted to ensure good balance effect.
The technical scheme for realizing the functions is as follows: a new lightweight complete dynamic balance mode and device for a double-shaft four-point high-speed press are characterized in that:
the four-point crank sliding block double-shaft balancing mechanism comprises a frame, a movable cross beam, a double-shaft four-point crank sliding block executing mechanism and a dynamic balancing mechanism; the movable cross beam is arranged on the frame and can move up and down along the guide rail of the frame to adjust the die filling height, and the double-shaft four-point crank slide block actuating mechanism is arranged on the movable cross beam through a bearing seat.
The double-shaft four-point crank sliding block executing mechanism comprises a first crankshaft and a second crankshaft, one end of a first connecting rod and one end of a second connecting rod are hinged to the first crankshaft, and the other end of the first connecting rod and the other end of the second connecting rod are hinged to a sliding block. One end of the third connecting rod and one end of the fourth connecting rod are hinged with the second crankshaft, and the other end of the third connecting rod and the other end of the fourth connecting rod are hinged with the sliding block.
The dynamic balance mechanism comprises a first auxiliary connecting rod, a second auxiliary connecting rod, a third auxiliary connecting rod and a fourth auxiliary connecting rod; one ends of the first auxiliary connecting rod and the second auxiliary connecting rod are hinged with the first crankshaft, the other ends of the first auxiliary connecting rod and the second auxiliary connecting rod are hinged with the auxiliary sliding block, one ends of the third auxiliary connecting rod and the fourth auxiliary connecting rod are hinged with the second crankshaft, the other ends of the third auxiliary connecting rod and the fourth auxiliary connecting rod are hinged with the auxiliary sliding block, and the auxiliary sliding block can reciprocate up and down along the guide rail. The first gearwheel and the second gearwheel are fixedly arranged on the first crankshaft and are respectively meshed with the first eccentric pinion and the second eccentric pinion, and the third gearwheel and the fourth gearwheel are fixedly arranged on the second crankshaft and are respectively meshed with the third eccentric pinion and the fourth eccentric pinion. First balancing weight, second balancing weight and third balancing weight fixed mounting are on first bent axle, and fourth balancing weight, fifth balancing weight and sixth balancing weight fixed mounting are on the second bent axle.
Further, the first gearwheel, the second gearwheel, the third gearwheel and the fourth gearwheel have the same structure, material and size, and the first eccentric pinion, the second eccentric pinion, the third eccentric pinion and the fourth eccentric pinion have the same structure, material and size. The eccentric pinion comprises a pinion, eccentric sheets and screws, and the eccentric sheets are symmetrically fixed on two sides of the pinion through the screws.
Furthermore, the first balancing weight, the second balancing weight, the third balancing weight, the fourth balancing weight, the fifth balancing weight and the sixth balancing weight have the same structure and comprise fixing rings, middle balancing weights, sealing gaskets and cover plates, a mounting hole is formed between each fixing ring and each middle balancing weight, an anti-skid wear-resistant layer and a key groove which are continuously distributed are arranged on the inner wall of the mounting hole and are matched with corresponding parts on the first crankshaft and the second crankshaft, and a plurality of cavities are formed in each middle balancing weight and can be used for filling media such as lead powder or iron powder.
Furthermore, the slide block can move up and down along the guide rail of the frame, when the high-speed press works, the rotating directions of the first crankshaft and the second crankshaft are opposite, and the structure, the material and the size of the first connecting rod, the second connecting rod, the third connecting rod and the fourth connecting rod are completely the same.
Further, the first, second, third and fourth secondary links have the same structure, material and dimensions as the first link.
Further, the unbalanced inertial forces of the first, second, third and fourth links are fully balanced by the first, second, third and fourth secondary links;
the auxiliary sliding block is light in weight relative to the sliding block, and a small part of unbalanced inertia force of the sliding block is balanced.
Furthermore, the first-order unbalanced inertial force of the sliding block is mainly balanced by a first balancing weight, a second balancing weight, a third balancing weight, a fourth balancing weight, a fifth balancing weight and a sixth balancing weight which are fixedly arranged on the first crankshaft and the second crankshaft; the second order unbalanced inertial force of the slider is balanced by means of a first eccentric pinion, a second eccentric pinion, a third eccentric pinion, and a fourth eccentric pinion fixedly mounted to the first crankshaft and the second crankshaft.
The invention has the advantages that:
(1) the invention adopts the auxiliary connecting rod, the auxiliary sliding block, the balancing weight and the balancing gear group to respectively balance the unbalanced inertia force of the connecting rod and the sliding block of the crank sliding block actuating mechanism, thereby obtaining good balancing effect;
(2) compared with a symmetrical inverted crank block dynamic balance mechanism, the dynamic balance mechanism adopted by the invention has greatly reduced mass;
(3) the counterweight block is internally provided with a plurality of cavities, can be used for filling media such as lead powder or iron powder and can adjust the counterweight mass; the quantity of the eccentric pieces on the eccentric pinion can be increased or decreased, so that the quality of the eccentric pinion is changed, and after the quality of the die on the sliding block is changed, the dynamic balance mechanism can still obtain a good balance effect.
Drawings
FIG. 1 is a front view of a high speed press of the present invention;
FIG. 2 is an isometric view of the dynamic balancing mechanism of the present invention (shown in phantom for ease of illustration, with the slider transparent);
FIG. 3 is a view taken from the direction A of FIG. 2 (with the slider transparent and shown in phantom for ease of illustration);
FIG. 4 is an exploded view of the counterweight;
FIG. 5 is a crankshaft structural view;
FIG. 6 is an isometric view of an eccentric pinion.
The reference numbers in the figures illustrate: 1. a frame; 2. a movable beam; 3. a double-shaft four-point crank slide block actuating mechanism; 4. a dynamic balancing mechanism; 5. a rack guide rail; 6. a bearing seat; 301. a first crankshaft; 302. a second crankshaft; 303. a first link; 304. a second link; 305. a slider; 306. a third link; 307. a fourth link; 401. a first secondary link; 402. a second secondary link; 403. a third auxiliary link; 404. a fourth auxiliary link; 405. a sub slider; 406. a guide rail; 407. a first bull gear; 408. a second bull gear; 409. a first eccentric pinion; 410. a second eccentric pinion; 411. a third bull gear; 412. a fourth bull gear; 413. a third eccentric pinion; 414. a fourth eccentric pinion; 415. a first weight block; 416. a second counterweight block; 417. a third counterweight block; 418. a fourth counterweight block; 419. a fifth balancing weight; 420. a sixth counterweight block; 4091. a pinion gear; 4092. an eccentric plate; 4093. a screw; 4151. a fixing ring; 4152, an intermediate counterweight body; 4153. sealing gaskets; 4154. and (7) a cover plate.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention. Thus, the following detailed description of the embodiments of the present invention, presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention.
Referring to fig. 1 to 6, a new lightweight and complete dynamic balance method and device for a double-shaft four-point high-speed press comprises a frame 1, a movable cross beam 2, a double-shaft four-point crank slider actuating mechanism 3 and a dynamic balance mechanism 4.
The movable cross beam 2 is arranged on the frame 1 and can move up and down along a frame guide rail 5 to adjust the die filling height, and the double-shaft four-point crank slide block actuating mechanism 3 is arranged on the movable cross beam 2 through a bearing seat 6.
The double-shaft four-point crank block actuating mechanism 3 comprises a first crank shaft 301 and a second crank shaft 302, wherein one end of a first connecting rod 303 and one end of a second connecting rod 304 are respectively hinged with the first crank shaft 301, and the other end of the first connecting rod is hinged with a slide block 305. One end of the third connecting rod 306 and one end of the fourth connecting rod 307 are hinged to the second crankshaft 302, and the other end is hinged to the slider 305. The slide block 305 can move up and down along the frame guide rail 5, when the high-speed press works, the first crankshaft 301 and the second crankshaft 302 rotate in opposite directions, and the first connecting rod 303, the second connecting rod 304, the third connecting rod 306 and the fourth connecting rod 307 are completely identical in structure, material and size.
The dynamic balance mechanism 4 comprises a first secondary connecting rod 401, a second secondary connecting rod 402, a third secondary connecting rod 403 and a fourth secondary connecting rod 404, and the structure, the material and the size of the first secondary connecting rod 401, the second secondary connecting rod 402, the third secondary connecting rod 403 and the fourth secondary connecting rod 404 are completely the same as those of the first connecting rod 303. One end of each of the first auxiliary connecting rod 401 and the second auxiliary connecting rod 402 is hinged to the first crankshaft 301, the other end of each of the first auxiliary connecting rod 401 and the second auxiliary connecting rod 402 is hinged to the auxiliary slider 405, one end of each of the third auxiliary connecting rod 403 and the fourth auxiliary connecting rod 404 is hinged to the second crankshaft 302, the other end of each of the third auxiliary connecting rod and the fourth auxiliary connecting rod is hinged to the auxiliary slider 405, and the auxiliary slider 405 can reciprocate up and down along the guide. The first gearwheel 407 and the second gearwheel 408 are fixedly mounted on the first crankshaft 301 and are engaged with the first eccentric pinion 409 and the second eccentric pinion 410, respectively, and the third gearwheel 411 and the fourth gearwheel 412 are fixedly mounted on the second crankshaft 302 and are engaged with the third eccentric pinion 413 and the fourth eccentric pinion 414, respectively. A first weight 415, a second weight 416, and a third weight 417 are fixedly mounted to the first crankshaft 301, and a fourth weight 418, a fifth weight 419, and a sixth weight 420 are fixedly mounted to the second crankshaft 302.
The first gearwheel 407, the second gearwheel 408, the third gearwheel 411 and the fourth gearwheel 412 are identical in structure, material and size, and the first eccentric pinion 409, the second eccentric pinion 410, the third eccentric pinion 413 and the fourth eccentric pinion 414 are identical in structure, material and size. The eccentric pinion gear comprises a pinion gear 4091, an eccentric sheet 4092 and screws 4093, wherein the eccentric sheet 4092 is symmetrically fixed on both sides of the pinion gear 4091 by the screws 4093.
The first balancing weight 415, the second balancing weight 416, the third balancing weight 417, the fourth balancing weight 418, the fifth balancing weight 419 and the sixth balancing weight 420 have the same structure and comprise a fixing ring 4151, a middle balancing weight 4152, a sealing gasket 4153 and a cover plate 4154, a mounting hole is formed between the fixing ring 4151 and the middle balancing weight 4152, an anti-skid wear-resistant layer and a key groove which are continuously distributed are arranged on the inner wall of the mounting hole and are matched with corresponding parts on the first crankshaft 301 and the second crankshaft 302, and a plurality of cavities are formed in the middle balancing weight 4152 and can be used for filling media such as lead powder or iron powder and the like.
The working principle of the invention is as follows:
(1) the principle that the dynamic balance mechanism provided by the invention obtains good balance effect is as follows:
the high-speed press machine adopts the double-shaft four-point crank sliding block actuating mechanism 3, and the left and the right are completely symmetrical, so that the inertia force in the horizontal direction is completely offset, and only the inertia force in the vertical direction exists. The vertical direction inertia force of the high-speed press consists of three parts, namely an unbalanced inertia force vertical component of a crankshaft, an unbalanced inertia force vertical component of a connecting rod and an unbalanced inertia force of a sliding block.
The crankshaft structure is a symmetrical structure as shown in fig. 5, and the center of mass is located at the rotation center of the crankshaft, so the unbalanced inertial force of the crankshaft is 0.
Secondly, the structure, material and size of the auxiliary connecting rod in the dynamic balance mechanism 4 are completely the same as those of the connecting rod in the actuating mechanism, when the high-speed press works, the motion acceleration of the auxiliary connecting rod and the connecting rod is equal in magnitude and opposite in direction, so that the inertia force can be completely offset, and the vertical component of the unbalanced inertia force of the connecting rod is completely balanced to be 0.
③ the unbalanced inertial force F of the slide block comprises mR omega2cos alpha (first order unbalanced inertial force), mR omega2λ cos2 α (second order unbalanced inertial force),
(third order unbalanced inertial force) and
(fourth order unbalanced inertial force) component, where α is the angle from the vertical during rotation of the crank.
In the formula, m represents the mass of the slider;
r-crank length;
omega-crank constant speed rotational angular velocity;
the included angle between the alpha-crank and the vertical direction;
lambda-link coefficient (crank length/link length).
Because the link coefficient λ of high speed presses is small (typically less than 0.1), the 3 α and 4 α components of the unbalanced inertial forces are negligible. Considering the motion accelerations of the sub-slider 405 and the slider 305, which are equal in magnitude and opposite in direction, the unbalanced inertial force of the slider is:
F＝(m-m1)Rω2(cosα+λcos2α)
in the formula, m1Secondary slideThe mass of the block.
The counter weight block and the bull gear are fixedly connected with the crankshaft, preferably, the transmission ratio between the bull gear and the meshed eccentric pinion is 0.5, so the inertia force of the six counter weight blocks is as follows: f1＝m2R1ω2cos alpha, the direction is opposite to the direction of the inertia force of the slide block; the inertia force of the six eccentric pinions is as follows: f2＝4m3R2ω2cos2 α, in a direction opposite to the slider inertial force.
In the formula, m2-the sum of the masses of six balancing weights;
R1-distance of the counterweight center of mass from the crankshaft center axis of revolution;
m3-the sum of the masses of the four eccentric pinions;
R2distance of eccentric pinion center of mass from its center of revolution
Through calculation, the mass m of the balancing weight is reasonably selected2And eccentric pinion mass m3So that:
(m-m1)Rω2cosα＝m2R1ω2cosα
(m-m1)λRω2cos2α＝4m3R2ω2cos2α
at this point, the inertial forces of the high speed press ram are fully balanced (leaving only minimal 3 α and 4 α components negligible).
In conclusion, the dynamic balance mechanism provided by the invention can achieve good balance effect.
(2) Compared with a symmetrical inverted crank block dynamic balance mechanism, the principle of reducing the weight of the dynamic balance mechanism is as follows:
from the foregoing analysis, it can be seen that the mass m of the auxiliary sliding block adopted in the invention is compared with the dynamic balance mechanism of the symmetrical inverted crank sliding block1Can be made small. Simultaneously, the distance R between the mass center of the balancing weight and the rotary central axis of the crankshaft is increased1And the distance R between the eccentric pinion center of mass and its rotation center2Can make the mass m of the balancing weight2And eccentricityPinion mass m3And is also small. Therefore, compared with a symmetrical reversed crank block dynamic balance mechanism, the weight of the dynamic balance mechanism can be greatly reduced.
(3) According to the invention, when the mass of the sliding block and the upper die changes, the dynamic balance mechanism can be adjusted, and the principle of ensuring good balance effect is as follows:
the middle counterweight body 4152 of the counterweight block adopted by the invention is internally provided with a plurality of cavities which can be used for filling media such as lead powder or iron powder, when the high-speed press works, the counterweight block rotates at high speed along with the crankshaft, and the media in the cavities are thrown away by centrifugal force, so that the mass center of the counterweight block is kept unchanged all the time. When the mass of the slide block and the upper die is changed, the cover plate 4154 can be opened, and iron powder or lead powder with corresponding mass is added or reduced into the cavity in the middle counterweight body 4152, so that the mass m of the counterweight block is changed2While the eccentric pinion mass m can be changed by increasing or decreasing the number of eccentric discs 40923And finally, the dynamic balance mechanism reaches new balance. Therefore, when the mass of the slide block and the upper die is changed, the dynamic balance mechanism can still obtain good balance effect.
The above description is only an embodiment of the present invention, and not intended to limit the scope of the present invention, and all equivalent structures or equivalent processes performed by the present specification and the accompanying drawings, or directly or indirectly applied to other related system fields, are included in the scope of the present invention.
Claims (8)
1. The utility model provides a complete dynamic balance device of lightweight for biax four point high-speed press which characterized in that:
comprises a frame (1), a movable cross beam (2), a double-shaft four-point crank slide block actuating mechanism (3) and a dynamic balance mechanism (4);
the movable cross beam (2) is arranged on the frame (1) and can move up and down along a frame guide rail (5) to adjust the die filling height, and the double-shaft four-point crank slide block actuating mechanism (3) is arranged on the movable cross beam through a bearing seat (6);
the double-shaft four-point crank block actuating mechanism (3) comprises a first crankshaft (301), a second crankshaft (302), a first connecting rod (303), a second connecting rod (304), a third connecting rod (306) and a fourth connecting rod (307);
one end of each of the first connecting rod (303) and the second connecting rod (304) is hinged with the first crankshaft (301), and the other end of each of the first connecting rod and the second connecting rod is hinged with the sliding block (305); one end of a third connecting rod (306) and one end of a fourth connecting rod (307) are respectively hinged with the second crankshaft (302), and the other ends of the third connecting rod and the fourth connecting rod are respectively hinged with a sliding block (305); the sliding block (305) can move up and down along the rack guide rail (5); the dynamic balance mechanism (4) comprises a first secondary connecting rod (401), a second secondary connecting rod (402), a third secondary connecting rod (403) and a fourth secondary connecting rod (404); one end of a first auxiliary connecting rod (401) and one end of a second auxiliary connecting rod (402) are respectively hinged with the first crankshaft (301), the other end of the first auxiliary connecting rod is respectively hinged with an auxiliary sliding block (405), one end of a third auxiliary connecting rod (403) and one end of a fourth auxiliary connecting rod (404) are respectively hinged with the second crankshaft (302), the other end of the third auxiliary connecting rod and the fourth auxiliary connecting rod are respectively hinged with the auxiliary sliding block (405), and the auxiliary sliding block (405) can reciprocate up and down along a guide rail (406);
a first gearwheel (407) and a second gearwheel (408) are respectively arranged at two ends of the first crankshaft (301), and the first gearwheel (407) and the second gearwheel (408) are respectively meshed with a first eccentric pinion (409) and a second eccentric pinion (410); a third gearwheel (411) and a fourth gearwheel (412) are respectively arranged at two ends of the second crankshaft (302), and the third gearwheel (411) and the fourth gearwheel (412) are respectively meshed with a third eccentric pinion (413) and a fourth eccentric pinion (414); the first crankshaft (301) is further provided with a first balancing weight (415), a second balancing weight (416) and a third balancing weight (417), and the second crankshaft (302) is provided with a fourth balancing weight (418), a fifth balancing weight (419) and a sixth balancing weight (420).
2. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to claim 1, characterized in that:
the first eccentric pinion (409), the second eccentric pinion (410), the third eccentric pinion (413) and the fourth eccentric pinion (414) are identical in structure and comprise pinions (4091), eccentric sheets (4092) and screws (4093), and the eccentric sheets (4092) are symmetrically fixed to two sides of the pinions (4091) through the screws (4093).
3. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to claim 1, characterized in that:
the first balancing weight (415), the second balancing weight (416), the third balancing weight (417), the fourth balancing weight (418), the fifth balancing weight (419) and the sixth balancing weight (420) are identical in structure and comprise a fixing ring (4151), a middle balancing weight body (4152), a sealing gasket (4153) and a cover plate (4154); a mounting hole is formed between the fixing ring (4151) and the middle balance weight body (4152), an anti-skid wear-resistant layer and key slots which are continuously distributed are arranged on the inner wall of the mounting hole and are matched with corresponding parts on the first crankshaft (301) and the second crankshaft (302), and a plurality of cavities are formed in the middle balance weight body (4152) and can be used for filling media.
4. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to claim 3, characterized in that:
the first connecting rod (303), the second connecting rod (304), the third connecting rod (306) and the fourth connecting rod (307) are completely the same in structure, material and size.
5. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to claim 4, characterized in that:
the first secondary connecting rod (401), the second secondary connecting rod (402), the third secondary connecting rod (403) and the fourth secondary connecting rod (404) are completely the same as the first connecting rod (303) in structure, material and size.
6. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to claim 5, characterized in that:
the first gearwheel (407), the second gearwheel (408), the third gearwheel (411) and the fourth gearwheel (412) are completely the same in structure, material and size, and the first eccentric pinion (409), the second eccentric pinion (410), the third eccentric pinion (413) and the fourth eccentric pinion (414) are completely the same in structure, material and size.
7. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to any one of claims 1 to 6, characterized in that:
the unbalanced inertial forces of the first link (303), the second link (304), the third link (306) and the fourth link (307) are completely balanced by the first secondary link (401), the second secondary link (402), the third secondary link (403) and the fourth secondary link (404);
the secondary slider (405) is lightweight relative to the slider (305) and balances out a small portion of the unbalanced inertial forces of the slider (305).
8. The lightweight complete dynamic balance device for the biaxial four-point high-speed press according to any one of claims 1 to 6, characterized in that:
the first-order unbalanced inertia force of the sliding block (305) is balanced by a first balancing weight (415), a second balancing weight (416), a third balancing weight (417), a fourth balancing weight (418), a fifth balancing weight (419) and a sixth balancing weight (420) which are fixedly arranged on the first crankshaft (301) and the second crankshaft (302); the second order unbalanced inertial force of the slider (305) is balanced by means of a first eccentric pinion (409), a second eccentric pinion (410), a third eccentric pinion (413) and a fourth eccentric pinion (414) which are fixedly mounted on the first crankshaft (301) and the second crankshaft (302).
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| CN112873985B (en) * | 2021-03-15 | 2023-12-15 | 苏州斯莱克精密设备股份有限公司 | Dynamic balance structure of double-acting high-speed press |
| CN114248483A (en) * | 2021-12-20 | 2022-03-29 | 重庆江东机械有限责任公司 | Main transmission structure of double-acting high-speed precision punch press |
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