JPS631060Y2 - - Google Patents

Description

[Detailed description of the invention] Fig. 1 shows an outline of a conventional hydraulic multi-disc clutch. A clutch drum 2' is provided on the input shaft 1' from the engine, and inside the clutch drum 2', a plurality of clutch plates 7' and a mating plate 6' are connected to a piston by a receiving plate 8' and a retaining ring 9'. The clutch is constructed to support the pressing force of ' and engage the clutch. The piston 5' is returned by a return spring 10', and a check ball 13' is installed to prevent oil in the piston chamber 15' from receiving centrifugal force and preventing the piston from returning. When the orifice 16' is opened and oil is delivered to the clutch chamber, the orifice 16' is closed. 3' and 4' are output gears which output power from the input shaft 1' when the respective clutches are engaged. 11', 12' are oil passages to the piston chamber, 14'
indicates the case.

In the conventional structure, the piston needs to move l' strokes before the clutch engages,
It has the following disadvantages: (1) The piston chamber is determined by the piston outer diameter and piston inner diameter, so it takes time to fill with oil, causing a time lag before the clutch engages. (2) At the end of the piston stroke, the entire surface of the piston becomes a pressure-receiving surface, and the piston pressing force increases even at low oil pressure, causing the clutch to suddenly engage and the shock to increase.

The present invention has been devised for the purpose of eliminating the above-mentioned drawbacks and developing a hydraulic clutch that can be smoothly engaged with little time lag.

The present invention relates to a hydraulic clutch that engages and disengages the clutch by a piston that reciprocates in the axial direction due to hydraulic pressure. a pressure receiving ring that slides to partition the oil chamber of the piston into an inner diameter oil chamber and an outer diameter oil chamber; and a pressure receiving ring that is provided on the pressure ring and communicates the inner diameter side oil chamber and the outer diameter side oil chamber. The hydraulic clutch is characterized by comprising an orifice and a pressure receiving surface formed on the pressure receiving ring, and the clutch piston is provided with a pressure receiving ring, and the piston chamber is divided into two, so that the clutch piston is moved and pressed. This is an attempt to provide a hydraulic clutch with a different size of pressure receiving surface, and is suitable for bulldozers,
It can be applied to power shift transmissions for cranes, forklifts, trucks, and automobiles.

An embodiment of the hydraulic clutch of the present invention will be described with reference to FIG. FIG. 2 shows a schematic diagram of an embodiment of the hydraulic clutch of the present invention. A clutch drum 2 is provided on the input shaft 1 from the engine, and inside the clutch drum, a plurality of clutch plates 7 and a mating plate 6 are engaged when pressed by the piston 3 to transfer power from the input shaft 1. It is incorporated so as to transmit the signal to the output gear 9. A pressure receiving ring 4 is slidably fitted into the piston 3 at its outer diameter portion, and is adapted to slide within the piston when hydraulic pressure is applied to the pressure receiving surface a or b. The oil chamber of the piston is partitioned by the pressure receiving ring 4 into an inner diameter oil chamber A and an outer diameter oil chamber B, which are communicated through an orifice C when the piston 3 moves by a stroke l. 5 is a check ball, 8 is a piston return spring, and 10 and 11 are oil passages.

The operation of the present invention will be explained.

(1) In the state shown in Fig. 2, when pressure oil is sent to the oil chamber A of the piston through the oil passage 10, the oil pressure acts on the pressure receiving surface a, and the pressure receiving ring is pushed to the right and hits the side wall of the clutch drum 2. While in the pressed state, the piston 3 receives hydraulic pressure on the pressure receiving surface up to the outer diameter of the pressure receiving ring, moves to the left, moves by a stroke l, and then presses the clutch plate to engage the clutch plate.

(2) At this point, the orifice C opens and the pressure oil flows into the outer oil chamber B, and the oil pressure also acts on the piston surface of the outer oil chamber B, making the entire piston surface a pressure receiving surface and tightening the clutch. Match. This completes clutch engagement.

(3) When the oil from the oil passage 10 is drained, the oil pressure in the inner oil chamber A drops instantly, and the oil pressure in the outer oil chamber B decreases to the inner side due to the return force of the return spring and the hydraulic pressure due to the centrifugal force. Since it is higher than the oil chamber A, the oil pressure acts on the pressure receiving surface b of the pressure receiving ring 4, causing the pressure receiving ring 4 to move toward the piston side, so that there is a sufficient gap between the pressure receiving ring 4 and the side wall of the clutch drum 2. The oil in the outer diameter side oil chamber B also drains smoothly. As a result, the piston quickly returns to its original position by the force of the return spring. That is, it will be in the position shown in FIG.

The present invention has the above configuration and has the following effects.

(1) When the clutch is engaged, it is only necessary to send oil to the inner diameter side oil chamber A until the piston stroke l during oil feeding, so the piston moves quickly and the time lag due to the piston stroke can be reduced.

(2) Since the pressure-receiving surface at the start of clutch engagement is small, the piston pressing force is small and the shock upon engagement is alleviated.

(3) After the clutch is engaged, oil is also sent from the orifice to the outer oil chamber B and is pushed by the entire surface of the piston, so the clutch exerts sufficient transmission force and prevents the clutch from slipping.

(4) When the clutch is released and the oil is drained, the oil in the outer oil chamber B does not return only from the orifice, but the movement of the pressure ring secures a large oil passage and the piston returns quickly, preventing poor clutch engagement and dragging. To prevent.

The above example is an example of a rotary hydraulic clutch;
Other hydraulic clutches (e.g. fusion, fixed)
Similar effects can be obtained in the case of .

[Brief explanation of drawings]

Figure 1 is a schematic diagram of a conventional hydraulic multi-disc clutch.
FIG. 2 shows a schematic diagram of an embodiment of the hydraulic clutch of the present invention. 1'...Input shaft, 2'...Clutch drum, 7'
...clutch plate, 6'...mating plate, 8'...receiving plate, 9'...retaining ring, 5'...piston, 10'...
...Return spring, 15'...Piston chamber,
13'...Check ball, 16'...Orifice, 3', 4'...Output gear, 11', 12'...Oil passage to piston chamber, 14'...Case, 1...Input shaft, 2 ...Clutch drum, 7...Clutch plate, 6...Mating plate, 3...Piston, 9...Output gear, 4...Pressure ring, a, b...Pressure receiving surface, A
...Inner diameter side oil chamber, B...Outer diameter side oil chamber, C...Orifice, 5...Check ball, 8...Return spring, 10, 11...Oil passage.

Claims (1)

[Scope of utility model registration request] In a hydraulic clutch that engages and disengages the clutch by a piston that reciprocates in the axial direction due to hydraulic pressure, the clutch is fitted into a fitting part provided on the hydraulic pressure receiving surface side of the piston so as to be able to reciprocate in the axial direction. a pressure receiving ring that divides the oil chamber of the piston into an inner diameter oil chamber and an outer diameter oil chamber; an orifice that is provided in the pressure ring and communicates the inner diameter oil chamber and the outer diameter oil chamber; and a pressure receiving surface formed on the pressure receiving ring.