JPH079584U - Counter type hydraulic press tuning device - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a tuning device for an opposed hydraulic press that does not require a tuning cylinder or a constant-quantity discharging device and can perform high cycle operation with less leak. [Structure] A piston-type first hydraulic cylinder 1 for driving a first slide S1, and a ram-type second liquid for driving a second slide S2, which is arranged so as to face the first slide S1. The pressure cylinder 2, the communication conduit 10 that connects the rod-side fluid chamber of the first hydraulic cylinder 1 and the oil chamber of the second hydraulic cylinder 1, and the head-side fluid chamber of the first hydraulic cylinder 1 Has a hydraulic pump P and an auxiliary cylinder for urging the second slide S2 in the return direction. The head side pressure receiving area A0 and the rod side pressure receiving area A1 of the first hydraulic cylinder 1 are provided.
Between the pressure receiving area A2 of the second hydraulic cylinder 2 and
= 2 · A1 = 2 · A2. The first hydraulic cylinder 1 may be a ram type.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a tuning device for an opposed hydraulic press. More specifically, the present invention relates to a hydraulic press having two slides arranged so as to oppose each other, and a tuning device for performing a pressurizing operation by synchronizing these two slides.

[0002]

[Prior art]

 The following is an example of a conventional tuning device in a hydraulic press. First, in the conventional example I shown in FIG. 5, the four-way switching valve 101 drives the tuning cylinder 102, and the working oil is discharged from the tuning cylinder 102 at the same flow rate and pressure, and the opposing hydraulic cylinders 103 and 104 having the same shape are opposed to each other. The oil is supplied to the oil chambers 105 and 106 on the head side.

In the conventional example II shown in FIG. 6, two rod rod cylinders 107 and 108 are arranged so as to face each other, and the oil chamber 109 on the pressurizing side of 107 of one cylinder and the oil chamber on the returning side of the other cylinder 108 are arranged. 110 is connected to a four-way switching valve 114, and the return-side oil chamber 112 of the one cylinder 107 and the pressurizing-side oil chamber 113 of the other cylinder 107 are connected to the four-way switching valve 114.

Further, in a conventional example III shown in FIG. 7, two hydraulic cylinders 122 and 123 are simultaneously reciprocally driven by a constant amount discharge device 130, and two slides 124, which oppose each other, are driven by the hydraulic cylinders 122 and 123. In this system, equal amounts of hydraulic oil are sent to the drive cylinders 126 and 127 provided on the 125 to perform synchronous drive.

[0005]

[Problems to be solved by the device]

 In the case of the conventional example I using the tuning cylinder 102 of FIG. 5, it is necessary to provide a cylinder having a capacity equal to or larger than that of the hydraulic cylinders 103 and 104 facing each other as the tuning cylinder 102, and the entire apparatus becomes large-scale. Furthermore, the two hydraulic cylinders 103, 104 and the tuning cylinder 102 both require high machining accuracy. Therefore, it is not suitable for presses with large processing capacity.

In the conventional example II in which the two rod cylinders 107 and 108 of FIG. 6 are connected in series, the synchronous circuit is configured by using only two cylinders of the same shape. However, the cylinder is a piston type double rod cylinder. Since it is necessary to use, there are 6 seals, and it is necessary to pay attention to pressure oil leakage. Moreover, in this type of device, the pressure applied to both rod cylinders 107 is the product (A · Pa) of the pressure Pa in the oil chamber 109 on the pressurizing side and the pressure receiving surface area A (note that the return side The pressure in the oil chamber 112 is "0"), and the pressure applied to both rod cylinders 108 is the pressure Pa in the return-side oil chamber 110 and the pressure in the pressurizing-side oil chamber 113 (= pressure of the hydraulic pressure source) Ps. Is the product of the pressure receiving area A and the difference (A (Ps-Pa)), so the pressure conditions are completely different between the two cylinders. Therefore, it is not suitable for high cycle operation.

Further, when a constant-quantity discharge device is used as in Conventional Example III in FIG. 7, the stroke of the cylinder is fixed, and the pressurizing force that can be generated is a function of the stroke. There is a problem that the adjustment is free and the maximum pressure is generated at any position of the stroke.

In view of the above-mentioned circumstances, the present invention utilizes the above-mentioned characteristics of hydraulic equipment, has the fewest number of components as possible, can be designed compactly, and can be used for a large press, and is an opposed type hydraulic suitable for high cycle operation. The object is to provide a press tuning device.

[0009]

[Means for Solving the Problems]

 The tuning device of the first invention drives (a) a first hydraulic cylinder of a piston type for driving a first slide, and (b) a second slide which is arranged to face the first slide. Ram type second hydraulic cylinder for the purpose of: (c) a communication conduit for connecting the rod-side hydraulic chamber of the first hydraulic cylinder and the hydraulic chamber of the second hydraulic cylinder; 1 hydraulic pressure: has a hydraulic pressure generation source that communicates with the liquid chamber on the head side of the cylinder, and (e) means for urging the second slide in the return direction, and (f) the first hydraulic cylinder The pressure receiving area A0 on the head side, the pressure receiving area A1 on the rod side, and the pressure receiving area A2 on the second hydraulic cylinder are characterized in that there is a relationship of A0 = 2.A1 = 2.A2.

The tuning device of the second invention is (a) a first hydraulic cylinder of a ram type for driving the first slide, and (b) a second slide arranged so as to face the first slide. A second hydraulic cylinder of a ram type for driving the hydraulic cylinder, and (c) a communication conduit for connecting the hydraulic chamber on the return side of the first hydraulic cylinder with the oil chamber of the second hydraulic cylinder; ) A fluid pressure generation source communicating with the fluid chamber on the operating side of the first fluid cylinder, and (e) means for urging the second slide in the return direction, and (f) the first fluid. The pressure receiving area A0 on the operating side of the pressure cylinder, the pressure receiving area A1 on the return side, and the pressure receiving area A2 of the second hydraulic cylinder have a relationship of A0 = 2.A1 = 2.A2. And

[0011]

[Action]

 According to the first invention, the pressure receiving area A1 on the rod side of the first hydraulic cylinder of the piston type and the pressure receiving area A2 of the head side of the second hydraulic cylinder of the ram type are equal, and the pressure receiving areas are given. Since the chambers communicate with each other, both hydraulic cylinders have opposite operating directions and equal strokes at any position. Therefore, synchronized operation can be achieved only by combining two cylinders and piping without using a homogenizing cylinder or a constant-quantity discharge device. As a result, the overall number of components is small, the unit is compact, and the processing accuracy does not need to be very high.

Further, since it is not necessary to use both rod cylinders and one cylinder is a ram type, only three sealing points are required. Therefore, there are few leaks. Further, when the piston is stopped by sandwiching the forged object between the slides, the pressure inside the liquid chamber on the rod side of the piston type cylinder and the pressure at the liquid pressure generation source become equal. Therefore, the pressure in the pressure chambers on both sides of the piston of the piston type cylinder becomes equal, and there is almost no leakage through the seal. Also, since the pressure conditions in both cylinders are almost the same, it is easy to maintain the balance, and therefore sufficiently follows the relatively high cycle operation.

In the second invention, a ram type cylinder is also used for the first cylinder. In this case, the same tuning action as in the first invention is exhibited, and since there is no piston, internal leakage does not occur and the cylinder There is an advantage that it is easy to increase the diameter.

[0014]

【Example】

 An embodiment of the tuning device of the present invention will be described below with reference to the drawings. FIG. 1 is a hydraulic circuit diagram showing an embodiment of a tuning device A of the first invention (the invention according to claim 1), and FIG. 2 is a sectional view showing an example of a hot forging press equipped with the tuning device of the first invention. 3 and 4 are hydraulic circuit diagrams of the hot forging press shown in FIG.

The tuning device A shown in FIG. 1 is equipped with a piston type hydraulic cylinder (hereinafter referred to as a first cylinder) 1 on one side, and is of a ram type (plunger type) so as to face the first cylinder 1. A hydraulic cylinder (hereinafter referred to as a second cylinder) 2 is provided. The first cylinder 1 has a rod 3 on only one side, and the outer diameter d of the rod 3 is (1/2) ^1/2 times the cylinder inner diameter D. Therefore, the pressure receiving area Ao on the head side is 1/4 · πD ² , and the pressure receiving area A 1 on the rod side is 1/4 · πD ² −1 / 4 · πd ² = 1/4 · π (D ² −1/2・ D ² ) = 1 / 4πD ² × 1/2 = 1 / 2Ao

On the other hand, the diameter of the ram 4 of the second cylinder 2 is the same as the outer diameter d of the rod 3 of the first cylinder 1, and the pressure receiving area A 2 is 1/4 · πd ² = 1/8 · πD ² = It becomes 1/2 · Ao. The mold for pressurizing the work is attached to the first slide S1 provided at the tip of the rod 3 of the first cylinder 1 and the second slide S2 provided at the tip of the ram 4 of the second cylinder 2, respectively.

The oil chamber 5 on the head side of the first cylinder 1 is switchably connected to a hydraulic pump P and a drain tank T via a four-way switching valve 6. In addition, 7 is a check valve, 8 is a 1st accumulator. The oil chamber 9 on the rod side of the first cylinder 1 communicates with the oil chamber 11 of the second cylinder 2 via a communication conduit 10. Further, a rod 13 of an auxiliary hydraulic cylinder 12 for returning is attached to the ram 4 of the second cylinder 2, and an oil chamber on the rod side of the auxiliary hydraulic cylinder 12 communicates with a second accumulator 15. Reference numeral 16 in FIG. 1 is a third accumulator for leak compensation, which is connected via a check valve 17 to the above-mentioned communication conduit 10 for communicating with the oil chamber.

In the tuning device A configured as described above, when the four-way switching valve 6 is in the state shown in FIG. 1, the head-side oil chamber 5 of the first cylinder 1 communicates with the drain tank T. . Therefore, the piston of the auxiliary hydraulic cylinder 12 is retracted by the action of the second accumulator 15, and the ram 4 of the second cylinder 2 is biased in the direction of arrow a to be retracted. As a result, the hydraulic oil in the oil chamber 11 of the second cylinder 2 flows into the rod-side oil chamber 9 of the first cylinder 1 through the pipe line 10, and the piston 18 is retracted in the direction of arrow b.

When the four-way switching valve 6 is switched from this state, the head-side oil chamber 5 of the first cylinder 1 communicates with the pump P, and the piston 18 is pushed out in the direction of arrow c. Then, the hydraulic oil in the oil chamber 9 on the rod side flows into the oil chamber 11 of the second cylinder 2 through the pipe line 10, and advances the ram 4 in the direction of arrow e.

At this time, the sectional area of the oil chamber 9 on the rod side of the first cylinder 1 (same as the pressure receiving area A1) and the sectional area of the oil chamber 11 of the second cylinder 2 (similar to the pressure receiving area A2) are the same. Therefore, the extension speed and extension amount of the rod 3 of the first cylinder 1 and the extension speed and extension amount of the ram 4 of the second cylinder 2 become the same, and synchronized operation is achieved.

Further, when the pressure generated by the pump P (and the accumulator 8) is PS and the internal pressure of the oil chamber 9 on the rod side is Pa, the pressing force F1 of the rod 3 of the first cylinder 1 is F1 = Ao. It is represented by Ps-A1.Pa. On the other hand, the pressing force F2 of the ram 4 of the second cylinder 2 is represented by F2 = A2.Pa. Here, A1 = A2 = Ao / 2, and the pressing forces F1 and F2 are reaction forces when pressing the same forging object, so that F1 = F2. Therefore, it can be seen that 2A1.Ps-A1.Pa = A1.Pa, and Ps = Pa.

The above relationship has an error due to fluid frictional resistance while the piston and the ram are moving, but is almost satisfied when the piston or the like is stopped or is moving very slowly. The fact that the pressure Ps from the pump P and the internal pressure Pa of the oil chamber 9 are equal as described above means that the pressure forces on both sides of the piston in the piston-type first cylinder 1 are substantially equal. Therefore, there is an advantage that oil does not leak beyond the seal around the piston. .

In the embodiment of FIG. 1, the cylinders of the first cylinder 1 and the second cylinder 2 are fixed, and the rod 3 and the ram 4 hold the first slide S1 and the second slide S2, respectively. In the press, it is preferable to fix the rod 25 and the ram as shown in FIG. 2 and move the cylinder so that it also serves as the slide.

The hot forging press shown in FIG. 2 has a frame-like frame 20 and first and second cylinders 20 which are slidably provided in holes 22 respectively formed in a pair of bases 21 facing each other of the frame 20. It has slides 23, 24 and fixed rods 25 and fixed rams 26 arranged in these slides 23, 24. The fixed rod 25 and the first slide 23 form a piston type first hydraulic cylinder, and the fixed ram 26 and the second slide 24 form a ram type second hydraulic cylinder. The outer end of the fixed rod 25 is fixed to a bracket 27, and the bracket 27 is fixed to the base 21 of the frame 20 by a tie rod 28. A piston 29 is attached to the inner end of the fixed rod 25, and the piston 29 is adapted to slide in the first slide 23. Reference numeral 30 is a rod cover, 31 is a piston packing, 32 is a metal bush, and 33 is a rod packing. As a result, the first slide 23 slides back and forth in the gap between the base 21 and the piston 29.

A first passage 35 communicating with the oil chamber 34 in front of the piston 29 and a second passage 37 communicating with the oil chamber 36 behind the piston 29 are formed from the bracket 27 to the fixed rod 25. Has been done. The outer end of the fixed ram 26 is fixed to a bracket 38, and the bracket 38 is fixed to the base 21 by a tie rod 39. Further, the inner side is slidably inserted into the second slide 24. Note that 40 is a rod packing and 41 is a metal bush. As a result, the second slide 24 slides between the base 21 and the fixed ram 26.

A flange 42 is formed at the rod-side end of the second slide 24, and the flange 42 is urged by a pair of auxiliary hydraulic cylinders 43 in the returning direction (arrow a direction). A third passage 45 is formed from the bracket 38 to the fixed ram 26, and communicates with an oil chamber 44 in front of the fixed ram 26. Further, a pump P as a pressure generating source is connected to the first passage 35, and a second passage 37 and a third passage 45 are connected by a communication pipe line 46.

FIG. 3 is a hydraulic circuit diagram of the opposed hot forging press described above. The pump P, the four-way switching valve 6, the first accumulator 8, the second accumulator 15, the third accumulator 15 and the like are shown in FIG. It is connected like a hydraulic circuit. Therefore, by switching the four-way switching valve 6, the first slide 23 and the second slide 24 reciprocate and the tuning operation is performed.

FIG. 4 is a hydraulic circuit diagram of the tuning device B according to one embodiment of the second device (the device according to claim 2). This embodiment is characterized in that a ram type (plunger type) hydraulic cylinder is used as the first cylinder 50, 54 is a ram of the first cylinder 50, 52 is an auxiliary hydraulic cylinder for returning, and its rod 53 is connected to the first slide S1, and the oil chamber on the rod side of the auxiliary hydraulic cylinder 52 is connected to the connecting pipeline 10. In this embodiment as well, the pressure receiving area A0 of the first cylinder 50 is twice the total pressure receiving area A1 of the pressure receiving areas of the two auxiliary hydraulic cylinders 52, and this total pressure receiving area A1 is the second cylinder. It is the same as the pressure receiving area A2 of D2. Therefore, the relationship of A0 = 2 · A1 = 2 · A2 is established. Since the configuration other than the above is substantially the same as that of the embodiment of FIG. 1, the same parts are designated by the same reference numerals and the description thereof will be omitted.

Therefore, in this embodiment as well, the same tuning action as that of the embodiment of FIG. 1 is exhibited, and since there is no piston in the first cylinder 50, internal leakage does not occur and it is easy to increase the diameter of the cylinder. There are advantages.

[0030]

[Effect of device]

 The opposed hydraulic press tuning device of the first invention has the advantage of the hydraulic cylinder that the stroke can be adjusted freely and that maximum pressure can be generated at any position of the stroke, and the number of components is small. , Compact. Also, since the number of packings is small, there is little leakage, and the pressure conditions of both cylinders are similar, making it suitable for high cycle operation. Further, it is not necessary to make the machining accuracy of the two cylinders so high, and therefore it is suitable for a large press.

In addition to the same tuning action as in the first aspect of the invention, the second aspect of the invention has the advantage that the first cylinder 50 has no piston so that internal leakage does not occur and the diameter of the cylinder can be increased easily. .

[Brief description of drawings]

FIG. 1 is a hydraulic circuit diagram showing an embodiment of a tuning device A of the first invention.

FIG. 2 is a sectional view showing an example of a hot forging press provided with the tuning device of the first invention.

FIG. 3 is a hydraulic circuit diagram of the hot forging press shown in FIG.

FIG. 4 is a hydraulic circuit diagram showing an embodiment of a tuning device B of the second invention.

FIG. 5 is a hydraulic circuit diagram showing an example of a conventional opposed hydraulic press.

FIG. 6 is a hydraulic circuit diagram showing another example of a conventional opposed hydraulic press.

FIG. 7 is a hydraulic circuit diagram showing another example of a conventional opposed oil press.

[Explanation of symbols]

A Tuning device 1 1st cylinder 2 2nd cylinder 3 Rod 4 Ram 10 Communication line P Pump 12 Auxiliary hydraulic cylinder S1 Slide S2 Slide 23 1st slide 24 2nd slide 25 Fixed rod 26 Fixed ram 43 Auxiliary hydraulic cylinder 46 Communication pipe Road 50 First cylinder 54 Ram

Claims (2)

[Scope of utility model registration request] 1. A piston-type first hydraulic cylinder for driving a first slide, and a ram for driving a second slide, which is arranged so as to face the first slide. A second hydraulic cylinder of a type, (c) a communication conduit that connects the rod-side hydraulic chamber of the first hydraulic cylinder and the oil chamber of the second hydraulic cylinder, and (d) the first hydraulic cylinder. A hydraulic pressure generation source that communicates with a hydraulic chamber on the head side; and (e) a means for urging the second slide in the return direction, and (f) a pressure receiving area on the head side of the first hydraulic cylinder. A0
And a pressure receiving area A1 on the rod side and a pressure receiving area A2 of the second hydraulic cylinder have a relationship of A0 = 2 · A1 = 2 · A2. . 2. A ram-type first hydraulic cylinder for driving a first slide, and a ram for driving a second slide, which is arranged so as to face the first slide. A second hydraulic cylinder of a type, (c) a communication conduit that connects the return-side hydraulic chamber of the first hydraulic cylinder and the oil chamber of the second hydraulic cylinder, and (d) the first hydraulic cylinder. A hydraulic pressure generating source communicating with the hydraulic chamber on the operating side; and (e) means for urging the second slide in the return direction, and (f) a pressure receiving area on the operating side of the first hydraulic cylinder. A0,
A tuning device for an opposed hydraulic press, wherein the pressure receiving area A 1 on the return side and the pressure receiving area A 2 of the second hydraulic cylinder have a relationship of A 0 = 2 · A 1 = 2 · A 2.