JPS5934723Y2 - Automatic reciprocating hydraulic system - Google Patents

Description

[Detailed description of the invention] Conventionally, a crank mechanism has been widely known as a reciprocating device, but it not only suffers from severe wear but also generates large noise and vibration, and is large because it must be driven by gears or belts. There were drawbacks such as.

Furthermore, in order to utilize a hydraulic cylinder in a reciprocating device, not only a separate switching valve is required, but also a driving device for the same is required.

The purpose of the present invention is to improve the above-mentioned drawbacks. One end of the piston rod 1 is slidably inserted into the sealed cylinder 9, and the piston portion 11 at the inner end of the piston rod 1 is inserted into the sealed cylinder 9. , a ring 10 that is in sliding contact with the inner peripheral surface of the cylinder 9 is slidably inserted, and the cylinder 9 is
The sliding range of the ring 10 is limited by a pair of stoppers 20, 20 provided on the inner peripheral surface of the piston rod 1, and an inlet oil passage 2 and a return oil passage 3 are bored in the piston rod 1. When the ring 10 slides, one of the oil guide passages 17 and 19 communicating with the outer periphery of the piston portion 11 from the oil return passage 3 and the oil return passage 3 connects to the circumferential groove 14 bored in the inner peripheral surface of the ring 10. The circumferential groove 14 is connected to the oil chamber 15b having a small pressure receiving area through an oil guide passage 18 bored in the ring 10, and the other side is closed. The oil chamber 15a is characterized in that it communicates with the oil chamber 15a via the feed oil passage 2 to form an operating circuit.

The present invention will be explained in more detail with reference to an example shown in the drawings. 1 is a piston rod in which an inlet oil passage 2 and a return oil passage 3 are bored, and the population of the inlet oil passage 2 is a relief valve 4.
The outlet of the feed oil passage 2 is connected to an oil tank 8 via a hose 7.

A ring 10 inscribed in the cylinder 9 is slidably attached to the piston portion 11 and is pressed by a spring 12 toward a rib 13 on the piston rod 1 side. An annular groove 14 is provided.

The feed oil passage 2 directly communicates with the oil chamber 15a on the side with the smaller pressure receiving surface through an oil guide hole 16, and communicates directly with the oil chamber 15a on the side with the larger pressure receiving surface.
5b communicates with the oil guide hole 17 through the annular groove 14 and the oil guide hole 18 bored in the ring, thereby making these oil guide holes 16, 17, and 18 communicate with each other. The feed oil passage 2 and the annular groove 14 form a differential circuit.

Further, an oil guide path 19 connected to the return oil path 3 is closed as the ring 10 slides, or is opened at a position where it communicates with the annular groove 14.

Furthermore, a pair of stoppers 20° 20 are provided on the inner circumferential surface of the cylinder 9 at intervals approximately equal to the reciprocating stroke, the piston rod 1 is fixed to a suitable machine frame, and the cylinder 9 is a reciprocating body. Pin 21' on the cutting blade 21
It is connected by .

Reference numeral 22 denotes a hydraulic cylinder for raising and lowering the reaping device, etc., which is provided at the front of the combine harvester. When the switching valve 24 is moved to the right in FIG. , moving it to the left will lower it.

25 is a clutch valve, and in the state shown in the figure, the cutting blade 21
is activated, and when it is moved to the right, it stops, and in this state, the hydraulic cylinder 22 is pushed up and activated.

In the above-mentioned device, the state shown in FIG. 1 is a state in which the cylinder 9 is moving toward the cutting blade side, and the hydraulic oil pumped from the hydraulic pump 6 pressurizes the left and right oil chambers 15b and 15a. Since the oil guide path 19 of the return oil path 3 is closed, the cylinder 9 moves toward the cutting blade 21 due to the difference in pressure receiving area, and the hydraulic oil in the right oil chamber 15a flows through the oil guide hole 16.17 and the annular groove. 14 and the oil chamber 15 on the left side through the oil guide hole 18.
flows into b.

During this time, the ring 10 is kept in its position by being pressed by the spring 12.

When the cylinder 9 moves in this way and the ring 10 contacts the right stopper 20 as shown in Fig. 2, the cylinder 9 moves further after contact due to the inertia of itself and the cutting blade 21, etc. 10 slides to the left side, and oil guide hole 1
At the same time as closing the oil guide hole 19 of the return oil passage, the annular groove 14 is closed.
It will be communicated to.

As a result, the hydraulic oil pumped by the hydraulic pump 6 is forced into one oil chamber 15a, and the hydraulic oil in the other oil chamber 15b returns to the oil passage through the oil guide path 18, the annular groove 14, and the oil guide hole 19. 3 and returns to the oil tank 8, and the cylinder 9 moves in the direction of pulling the cutting blade 21.

During this time, the ring 10 is pressurized only from the oil chamber 15a side, so the spring maintains a compressed state.

Next, when the ring 10 comes into contact with the left stopper 20, the state shown in FIG. 1 is returned, and the cylinder 9 moves toward the cutting blade 21, and eventually the cylinder 9 automatically repeats the reciprocating operation.

Note that when the cylinder 9 converts into reciprocating motion, the movable blade of the cutting blade 21 is superimposed on the fixed blade, so there is no cutting resistance and the movable blade operates smoothly.

Furthermore, if the diameter of the screw rod 1 is set to % of the inner diameter of the cylinder 9, the operating force and speed will be the same as the reciprocating motion.

Furthermore, although not shown, a bypass oil passage is provided between the hoses 5 and 7 or between the sending oil passage 2 and the return oil passage 3, and the valve attached to this passage is connected to a working machine clutch lever such as a reaping and conveying latch lever. - If the above-mentioned valve is opened when the cutting blade is stopped, the ring 10 will not be subjected to hydraulic pressure and will be pressed by the spring 12 and will be in the state shown in Fig. 1. The next drive can be performed smoothly.

Further, although the piston rod 1 is fixed in the illustrated example, the cylinder 9 may be fixed, and it goes without saying that the present invention can also be applied to a double-rod type by changing the diameter of the piston rod.

In the present invention, one end of the piston rod 1 is slidably inserted into the sealed cylinder 9 as described above, and a ring 10 is attached to the piston portion 11 at the inner end of the piston rod 1 and is in sliding contact with the inner peripheral surface of the cylinder 9. A pair of stoppers 20.2 are slidably inserted and provided on the inner peripheral surface of the cylinder 9.
0 to limit the sliding range of the ring 10, and the piston rod 1 is provided with an inlet oil passage 2 and a return oil passage 3. An oil guide path 17 communicating with the outer periphery of. 19 are deviated and bored so that when the ring 10 slides, one of them communicates with the circumferential groove 14 bored in the inner circumferential surface of the ring 10 and the other is closed, and the circumferential groove 14 is Oil guide path 1 bored in ring 10
8 communicates with the oil chamber 15b having a large pressure-receiving area and communicates with the oil chamber 15a having a small pressure-receiving area via the feed oil passage 2 to form an operating circuit. The driven body can be reciprocated using only an extremely compact hydraulic device without the need for a drive mechanism such as a belt or chain, and the transmission mechanism such as the speed change gear does not wear out or generate noise, making it light and easy to move. It is possible to reciprocate at high speed.

Furthermore, there is no need for a switching valve operated by power, and reciprocating motion can be automatically achieved simply by force-feeding hydraulic oil from one oil path, thereby significantly reducing manufacturing costs.

[Brief Description of the Drawings] The drawings show an example of the embodiment of the present invention.
2 and 2 are cross-sectional views of essential parts, and FIG. 3 is a hydraulic circuit diagram of the combine harvester. 1... Piston rod, 2... Feed oil path, 3... Return oil path, 6... Hydraulic pump, 5.・7...Hose, 9...Cylinder, 10...Ring, 12...Spring, 14...Annular groove, 15a, 15b
...Oil room, 16, 17.18.19...
・Oil guide hole.

Claims (1)

[Scope of utility model registration request] One end of the piston rod 1 is slidably inserted into the sealed cylinder 9, and a ring 1 is attached to the piston portion 11 at the inner end of the piston rod 1 so as to be in sliding contact with the inner peripheral surface of the cylinder 9.
A pair of stoppers 20, 20 provided on the inner peripheral surface of the cylinder 9 limit the sliding range of the ring 10, and the piston rod 1 is connected to the feed oil passage 2 and the return oil passage. 3 are bored and communicate with the outer periphery of the piston portion 11 from the feed oil passage 2 and the return oil passage 3, respectively.
19 are deviated and bored so that when the ring 10 slides, one of them communicates with the circumferential groove 14 bored in the inner circumferential surface of the ring 10 and the other is closed, and the circumferential groove 14 is The oil passage 18 bored in the crosspiece 10 communicates with the oil chamber 15b having a large pressure-receiving area, and the oil chamber 15a having a small pressure-receiving area communicates with the feed oil passage 2 to form an operating circuit. An automatic reciprocating hydraulic system featuring: