JP3313833B2 - Marine speed reducer - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates mainly to a mechanism for preventing the output shaft from rotating when the marine speed reducer is in the neutral position.

[0002]

2. Description of the Related Art Wet type multi-plate clutches are used in marine deceleration / reversing machines. For example, when a hydraulic clutch type deceleration / reversing device with two forward speeds and one reverse speed is equipped, a friction plate on the driving side of the hydraulic clutch is used. Lubricating oil is filled between the friction plate on the driven side and the friction plate on the driven side. Comparing the friction plate capacity as a whole, the ratio of the forward side to the reverse side is 2: 1, and the unbalanced forward and backward friction plate capacity is obtained. When the engine was rotated to a neutral position at a low engine speed, a drag phenomenon occurred, and the output-side propeller rotated forward and could not be completely stopped.

[0003] In view of the above, there have been conventionally proposed some skewing prevention mechanisms. For example, Japanese Utility Model Publication No. 63-4730
The lubricating oil is supplied to the hydraulic clutch as in the technology disclosed in Japanese Patent Application Laid-Open No. 9-94, for example, by operating the hydraulic brake at the time of neutral operation to forcibly stop the output shaft, or in the technology disclosed in Japanese Utility Model Publication No. 1-46888. At low engine speeds, lubricating oil was supplied in a small amount so as to eliminate the dragging phenomenon, so that the amount to be performed was inversely proportional to the engine speed.

[0004]

However, in the case of a configuration in which a brake that operates during neutral operation is provided, an extra brake device must be provided, which increases the cost and the space thereof. Further, a governor device is required to make the amount of the lubricating oil inversely proportional to the engine speed, and the provision of this device also requires a space, which is a factor of high cost.

[0005]

The present invention uses the following means to solve the above-mentioned problems. In a deceleration reversing machine having a hydraulic clutch whose forward gear is larger than the number of reverse gears and shifting by operating the forward / backward switching valve 23 , the hydraulic pump 25 and the forward / backward switching valve 2
3 , a resistance valve 24 is provided, and the resistance valve 24 and forward / backward switching are switched.
Together configured to enable oil feed lubricating oil to the hydraulic clutches before and after via the regulating valve 29 from between the valve 23 and further, the reverse through the distribution valve 40 from between the hydraulic pump 25 and the resistor valve 24 clutch R The lubricating oil can be supplied to the reverse clutch R which supplies oil via the distribution valve 40 at the time of neutrality .
Lubricating oil pressure so that the output shaft does not rotate
The spring pressure of the resistance valve 24 is adjusted so that

[0006]

By using such means, when the forward / reverse switching valve 23 is switched to neutral, the hydraulic clutch F
1 · F2 · R hydraulic oil, adjustment valve 29, distribution valve 40
Is communicated to the tank 39, and the pressure oil is sent to the lubricating oil passages 19, 20, and 21 via the adjusting valve 29, and is simultaneously sent to the lubricating oil passage 21 of the reverse clutch via the distribution valve 40. You. The oil pressure of the lubricating oil in these two directions is set by the resistance valve 24. At the time of shipment, the lubricating oil pressure of the forward first speed clutch F1 and the forward second speed clutch F2 and the lubricating oil pressure of the reverse clutch R are balanced. The rotation of the output shaft 10 is stopped at the neutral position.

[0007]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. FIG. 1 shows a hydraulic clutch-type two forward speed, one reverse speed deceleration / reversing device and its hydraulic circuit configuration, and three clutch shafts 1, 2, and 3 are horizontally mounted on a transmission case.
Input gears 4a, 5 are provided on the clutch shafts 1, 2, 3 respectively.
The clutch housings 4, 5, and 6 having the clutch housings 4, 5, and 6 are externally fitted, and power is transmitted from an engine (not shown) to any one of the input gears.
Is fitted with a driving-side friction plate.

Output gears 7, 8, 9 are rotatably supported on the clutch shafts 1, 2, 3 and mesh with a drive gear 11 on the output shaft 10. The driven side friction plates are externally fitted so as to be alternately arranged with the driving side friction plates, lubricating oil is filled between the friction plates, and the friction plates are pressed by the pistons 13, 14 and 15 to transmit power. Enabled, and each forward first-speed clutch F
1, a forward second speed clutch F2 and a reverse clutch R are configured, and by operating the respective hydraulic clutches,
Power from the engine is transmitted to the output shaft 10 so that the fixed propeller 12 can be rotated and propelled.

The clutch housings 4, 5, 6 have oil passages 16, 17, 18 for supplying hydraulic oil for driving the pistons 13, 14, 15 and oil passages 19, 2 for supplying lubricating oil.
The first and second forward clutches F1 and F2 are connected to the oil passages 16 and 17 of the hydraulic oil of the second forward clutch F2 through a switching valve 22 to enable two-stage forward switching. The pump port 22 and the hydraulic passage 18 for the hydraulic oil of the reverse clutch are respectively connected to an output port of a forward / reverse switching valve 23, and the pump port of the forward / reverse switching valve 23 is connected to a hydraulic pump 25 via a resistance valve 24. ing.

An oil passage 26 is branched from between the resistance valve 24 and the forward / reverse switching valve 23, and a pressure gauge 27 is provided at this branch portion. The adjustment valve 29, the oil cooler 30, It is connected to the lubricating oil passages 19, 20 and 21 through a vessel 31 and throttles 32, 32 and 32. 33 is an alarm switch, 34 is a lubricating oil pressure regulating valve, and 35 is a pressure gauge.

A branch oil passage 36 and a relief valve 37 are connected between the resistance valve 24 and the hydraulic pump 25. The relief valve 37 returns a hydraulic pressure equal to or more than a specified value to the tank 39. The distributing valve 40 communicates with the lubricating oil passage 21 of the reverse clutch. And
The output port A of the forward / reverse switching valve 23 is connected to the control ports S1 and S2 of the regulating valve 29 and the distribution valve 40.

In such a configuration, in a state where the forward / reverse switching valve 23 is switched to the forward direction and the switching valve 22 is switched to the first forward speed, the hydraulic oil from the hydraulic pump 25 is supplied from the resistance valve 24 to the forward / reverse switching valve 23. Then, pressure oil is sent to the oil passage 16 via the switching valve 22 and pushes the piston 13 to drive the propeller 12 with the forward first speed clutch F1 in the "contact" state. On the other hand, the lubricating oil passage 19 and the tank 39 communicate with each other. Then, also in the case of the second forward speed, the pressure oil is similarly supplied to the oil passage 17 and the propeller 12 is driven by setting the second forward speed clutch F2 to “contact”. Further, in the case of the reverse speed, the forward / reverse switching valve 23 is switched, the oil is supplied to the oil passage 18 and the piston 14 is pushed to make the reverse clutch R “closed” to rotate the propeller 12 in the reverse direction.

When the vehicle is moving forward and backward, the pressure oil from the output port A is sent to the control ports S1 and S2 of the regulating valve 29 and the distribution valve 40. The regulating valve 29 is closed by the pressure, and the distribution valve 40 is switched against the spring 40a so that the lubricating oil passage 2
Disables oil supply to 1.

When the forward / reverse switching valve 23 is switched to a neutral position, the hydraulic oil passages 16, 17, and 18 of the piston,
And, the control ports S1 and S2 are communicated with the tank 39,
The lubricating oil passages 19, 20,.
The oil is fed to the lubricating oil passage 21 of the reverse clutch R from the oil passage 36 via the distribution valve 40 at the same time.

The oil pressure of the lubricating oil from the hydraulic pump 25 to the oil passage 26 and the oil passage 36 is set in the resistance valve 24. This setting is performed by rotating the screw of the spring 24a by rotating the screw. The first forward clutch F1 and the second forward clutch F2 can be set at the time of shipment.
Is adjusted so that the lubricating oil pressure of the reverse clutch R and the lubricating oil pressure of the reverse clutch R are balanced, and the force of the output shaft 10 to rotate forward and the force of the reverse rotation cancel each other, and the rotation of the output shaft 10 stops at the neutral position. It is done.

[0016]

The present invention has the following advantages because it is constructed as described above. That is, it is possible to stop the rotation of the output shaft at the neutral position only by improving the piping and adjusting the set pressure of the resistance valve, so that it is not necessary to provide a neutral brake or a governor device as in the related art. Thus, a low-cost drag prevention mechanism can be obtained.

[Brief description of the drawings]

FIG. 1 is a hydraulic clutch type deceleration / reversing device of a second forward speed and a first reverse speed, and a hydraulic circuit diagram thereof.

[Explanation of symbols]

 F1 Forward first speed clutch F2 Forward second speed clutch R Reverse clutch 19, 20, 21 Lubricating oil passage 23 Forward / backward switching valve 24 Resistance valve 25 Hydraulic pump 29 Adjusting valve 40 Distribution valve

Continuation of the front page (56) References JP-A-4-50517 (JP, A) JP-A-4-5554 (JP, U) JP-A-1-167997 (JP, U) JP-A 64-44895 (JP) , U) Japanese Utility Model Showa 64-10499 (JP, U) Japanese Utility Model Showa 60-2047 (JP, U) Japanese Utility Model Showa 59-132943 (JP, U) Japanese Utility Model 63-47309 (JP, Y1) Japanese Utility Model 1-42688 (JP, Y2) (58) Fields investigated (Int. Cl. ⁷ , DB name) B63H 23/30 F16D 25/14 F16H 57/04

Claims (1)

(57) [Claims] 1. A forward gear stages can have more hydraulic clutches than reverse shift stages, before the reverse and reduction gear for shifting the operation of the reverse switching valve 23, the resistance valve between the hydraulic pump 25 and the forward-reverse switching valve 23 24 is provided, as well as oil feed configured to be capable of lubricating oil to the hydraulic clutches before and after via the regulating valve 29 than during the forward-reverse switching valve 23 and the resistive element defense 24, further wherein the hydraulic pump 25 and the resistor valve 24 reverse click the lubricating oil is configured to be oil feed to the reverse clutch R via the distribution valve 40 from between, the neutral state, feeding oil through the distribution valve 40
The lubrication oil pressure to the latch R prevents the output shaft from rotating.
Adjust the spring pressure of the resistance valve 24 so that the lubrication oil pressure becomes
Marine reverse and reduction gear, characterized in that that.