JP3279824B2 - Hydraulic passage structure of pressure oil transfer section - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an oil passage structure of a hydraulic oil receiving portion used for a reversible hydraulic clutch mechanism or the like provided at the rear of a marine engine.

[0002]

2. Description of the Related Art Conventionally, a drill hole is directly formed in a transfer cylinder or a joint to independently form an oil passage. However, the spacer is lengthened by the amount of the entire bored oil passage, which causes the shaft to be long.

[0003]

SUMMARY OF THE INVENTION The present invention is configured so that one oil passage can be completed by completing the assembly of two parts in a butted state. This makes it possible to reduce the length of the shaft in which the oil passage is drilled, and when one input joint 39 is fixed to the input shaft 1 by hydraulic fitting, the input cylinder 39 Since the fixing between the joints 39 is completely performed, the cut oil passage 2 is connected to the input joint 3.
9 is completely closed by the end face 39a. Thus, the configuration of the oil passage is simplified, and the length of the shaft is reduced.

[0004]

Means for Solving the Problems The present invention is configured as follows to solve the above-mentioned problems. Claim 1
In addition, on the outer periphery of the input shaft 1 in which the radial oil passage 12 is bored,
The transfer cylinder 38 and the input joint 39 are fixed, and a fixed-side seal case 42 is fitted around the outer circumference of the transfer cylinder 38 and the input joint 39, and the oil of the transfer cylinder 38 or the input joint 39 is removed from the fixed-side seal case 42. via the road, in a configuration for supplying a pressure oil to the inside of the radial oil passage 12 of the input shaft 1, taking over tube 38 and inlet
The cut oil passage 2 is formed at one of the butting portions of the force coupling 39.
And closing the cut oil passage 2 at the end face of the input joint 39.
Constitutes an inherited oil passage, and
On the outer periphery, an outer peripheral oil passage 7 communicating with the cut oil passage 2 is engraved,
Perforated in the outer peripheral oil passage 7 and the fixed side seal case 42
Communicates with the drilling oil passage 17 and abuts the transfer cylinder 38
An inner oil passage 18 communicating with the cut oil passage 2 is provided on the inner periphery of the set portion.
Engraved and drilled in the inner oil passage 18 and the input shaft 1.
The oil passage 12 is communicated with the oil passage 12 . Claim 2
In the oil passage structure of the pressure oil receiving portion according to claim 1,
Fitted on the outer periphery of the input shaft 1 on the side opposite to the input joint 39
Turn off the lubricating oil passage 4 that supplies the lubricating oil to the roller bearing 21.
A drill hole is drilled in the transfer cylinder 38 from the oil passage 2 and the lubrication
A throttle hole 4a is formed at the end of the oil passage 4 on the roller bearing 21 side.
It has been achieved.

[0005]

Next, the operation will be described. Since the lubricating oil passage is formed by the cut oil passage 2 and the butted end surface 39a, the transfer cylinder 38
It is no longer necessary to provide a complete drilling oil passage, and the cut-off oil passage 2 is sufficient, so that the length of the transfer cylinder 38 can be shortened, whereby the length of the input shaft 1 can be shortened. It was done. In addition, the cost can be reduced by using a simple oil passage.

[0006]

Next, an embodiment will be described. FIG. 1 is an overall view of a reversible rotary hydraulic clutch mechanism attached to the rear of a marine engine provided with an oil passage structure of a pressure oil receiving portion according to the present invention, and FIG. 2 is fixed to an input shaft 1, a receiving cylinder 38, an input joint 39 and 3 is an enlarged cross-sectional view of a portion of the side seal case 42, FIG. 3 is an enlarged cross-sectional view of a portion forming an oil passage in an end surface abutting state only between the transfer cylinder 38 and the input joint 39, and FIG. Cut oil passage 2 provided on the end face
FIG. 5 is a side view of the transfer cylinder 38, and FIG. 6 is a cut-in oil path 2, an outer oil path 7, and an inner oil path on the end face side of the transfer cylinder 38. It is a drawing showing a road 18.

Referring to FIG. 1, the overall structure of a reversible hydraulic clutch mechanism provided at the rear of a marine engine will be described.
While transmitting the power from the flywheel 37 of the engine to the output joint 51, a forward hydraulic clutch device having a forward friction plate mechanism 6 and a reverse friction plate mechanism 5 were provided inside the clutch case 50. A reverse hydraulic clutch device and a planetary gear type reverse rotation mechanism are arranged. The forward hydraulic clutch device is arranged and configured on the outer periphery of the output shaft 52, and the reverse hydraulic clutch device is overlapped at a position on the outer periphery of the forward hydraulic clutch device. The forward hydraulic clutch device and the reverse hydraulic clutch device are arranged in parallel at the overlapped portion, and a planetary gear type reversing mechanism composed of a carrier 8 and a pinion is arranged in series on the outer periphery of the rear portion of the output shaft 52.

The engine is arranged on the front surface of the flywheel 37, and the rubber block ring 10 is fixed to the rear surface of the flywheel 37. A rubber block slider 9 is interposed in the rubber block ring 10 via a vibration-proof elastic body. By interposing an anti-vibration elastic body between the rubber block ring 10 and the rubber block slider 9, an impact mitigation mechanism is configured. The rubber block slider 9 is fixed to an input joint 39. The input joint 39 is locked to the input shaft 1 by hydraulic fitting, and the input joint 39 and the transfer cylinder 38 are in close contact with each other.

The transfer cylinder 38 is also fixed to the input shaft 1 and can rotate together. A fixed-side seal case 42 is fitted around the transfer cylinder 38, and a lubricating oil passage and a forward oil passage are connected to the fixed-side seal case 42 from a hydraulic pressure switching valve by piping. The fixed side seal case 42
The oil passage communicates with the oil passage of the transfer cylinder 38 in a state where the transfer cylinder 38 is rotatable and the fixed-side seal case 42 is fixed. The oil passage to the reverse hydraulic clutch device is not bored in the input shaft 1 because oil is sent from the clutch case 50 toward the fixed side of the outer periphery of the reverse hydraulic clutch device.

The input shaft 1 and the output shaft 52 are
2, the bearings are supported on the same shaft so as to be rotatable differently. A forward hydraulic clutch device is arranged in a donut shape on the outer periphery of the output shaft 52, and a reverse hydraulic clutch device is arranged in a donut shape in parallel with the outer periphery of the forward hydraulic clutch device. At the rear of the output shaft 52, a planetary gear type reversing mechanism constituted by a carrier 8 and a pinion in series with the parallel portion of the forward hydraulic clutch device and the reverse hydraulic clutch device is arranged.

The output shaft 52 is first pivotally supported with respect to the input shaft 1 by a small-diameter conical roller bearing 48, and is then supported in a double row by a large-diameter conical roller bearing 49 at a subsequent stage. The large diameter conical roller bearing 49 is covered with an output shaft cover 59. An output joint 51 is fixed to a portion where the output shaft 52 protrudes from the clutch case 50. The planetary pinion and the reverse rotation pinion are pivotally supported by a planetary gear shaft and a reverse planetary gear shaft provided on the carrier 8, and an inspection window 50 is provided on a clutch case 50 for facilitating inspection, repair, and replacement of these planetary gears.
a is provided.

A hydraulic oil pump 40 is fixed to a front surface of the clutch case 50. The hydraulic oil pump 40 is driven by a pump shaft 41. Pressure oil from the pump shaft 41 is supplied to a forward hydraulic clutch device and a reverse hydraulic clutch device via a switching control valve. The pump shaft 41 is driven by the pump gear 31.

Next, a specific configuration of the present invention will be described with reference to FIGS. 2, 3, 4, 5, and 6. FIG. According to the present invention, the cut-off oil passage 2 is engraved on a transfer cylinder 38 fitted and fixed on the outer periphery of the input shaft 1, and the cut oil passage 2 is opened at the end face of the transfer cylinder 38 as a non-blocking oil passage. It is engraved. The semi-closed cutting oil passage 2 is closed by an input joint 39 fitted to the front portion of the transfer cylinder 38 by hydraulic fitting.
Is the butted end surface 39a of the rear surface.

The transfer cylinder 38 is provided with a drilling oil passage 3 for supplying pressure oil to the forward hydraulic clutch device. The drilling oil passage 3 communicates with the drilling oil passage 16 of the fixed-side seal case 42 and also communicates with the radial oil passage 14 of the input shaft 1. The radial oil passage 14 communicates with an axial oil passage 15 of the input shaft 1. The axial oil passage 15 supplies pressure oil to a hydraulic cylinder 20 of the forward hydraulic clutch device.

The oil passage constituted by the cut oil passage 2 of the present invention communicates with the perforated oil passage 17 of the fixed-side seal case 42, passes through the cut oil passage 2, and passes through the radial oil passage of the input shaft 1. Communicates with 12.
The radial oil passage 12 communicates with the axial oil passage 13, and discharges lubricating oil to the inside of the forward friction plate mechanism 6, the inside of the reverse friction plate structure 5, or to each gear of the planetary gear type reversing mechanism. are doing. Reference numeral 21 denotes a roller bearing, which is interposed between the input shaft 1 and the clutch case 50. The roller bearing 2
The transfer cylinder 38 is configured as a spacer fitted between the input joint 1 and the input joint 39.

As shown in FIG. 4, FIG. 5, and FIG.
The lubricating oil passage 4 to the roller bearing 21 is formed in one of the notching oil passages 2 as a drill hole. As shown in FIG. 3, the end of the lubricating oil passage 4 on the roller bearing 21 side is formed as a throttle 4 a, which has a throttle structure so that the lubricating oil is not discharged only to the roller bearing 21 at a stroke. Have been. In addition, since there is only one radial oil passage 12 drilled in the input shaft 1, it is difficult to make the radial oil passage 12 and the cut oil passage 2 communicate with each other in alignment with each other. In order to eliminate the need for complete alignment between the mechanism 6 and the radial oil passage 12, the transfer cylinder 38
The inner circumference oil passage 18 is engraved on the inner circumference.

In addition, the transfer cylinder 3 is formed so that the cut oil passage 2 having only two cuts and the perforated oil passage 17 of the fixed-side seal case 42 are always in communication during rotation of the input shaft 1.
An outer peripheral oil passage 7 is engraved on an outer peripheral portion of 8. The outer peripheral oil passage 7 and the inner peripheral oil passage 18 communicate with each other via the cut oil passage 2. Further, seal grooves 23, 23, 23, 23 are formed on the outer periphery of the transfer cylinder 38 so as to prevent leakage of pressure oil between the drilling oil passages 3 and the forward friction plate mechanism 6. The input joint 39 is also provided with a seal groove 22 on the outer periphery for preventing leakage of pressure oil. Reference numeral 24 denotes a labyrinth groove, which guides oil leaking from 22 to the case. Further, in FIG. 3, a lubricating oil passage 25 is formed between the seal grooves 23 to prevent wear of the outer seal ring.

[0018]

As described above, the present invention has the following advantages. Since the lubricating oil passage is constituted by the cut-in oil passage 2 and the butt end surface 39a as in claim 1, it is not necessary to provide a complete drilling oil passage in the transfer cylinder 38, and the cut-in oil passage 2 suffices. The length of the transfer cylinder 38 can be reduced, and the length of the input shaft 1 can be reduced. Also, input shaft 1
Since only one radial oil passage 12 is bored,
It is difficult to make the oil passage 12 and the cut oil passage 2 communicate with each other.
Although it is difficult, the inner circumference oil passage 18 is engraved on the inner circumference of the transfer cylinder 38.
During assembly, the friction plate mechanism 6 for forward movement and the diameter
It is necessary to take an alignment state that perfectly matches the directional oil passage 12.
It is gone. In addition, the cost can be reduced by using a simple oil passage. Claim
2, the cutting oil passage 2 is located at the center of the transfer cylinder 38.
Two notches are cut at 180 ° and the cuts
The lubricating oil passage 4 to the roller bearing 21 is cut in one of the oil passages 2.
Since it is drilled as a hole,
The lubrication of the roller bearing 21 is performed by the cut oil passage 2 and the lubrication oil passage 4.
It can be done through. The lubricating oil passage
The end of the roller bearing 21 on the side of the roller bearing 21 is a throttle 4
a, and only the roller bearing 21
Lubricating oil could not be discharged
Things.

[Brief description of the drawings]

FIG. 1 is an overall view of a reversible rotary hydraulic clutch mechanism attached to a rear part of a marine engine having an oil passage structure of a pressure oil receiving portion according to the present invention.

FIG. 2 is an enlarged sectional view of a portion including an input shaft 1, a transfer cylinder 38, an input joint 39, and a fixed-side seal case 42.

FIG. 3 is an enlarged cross-sectional view of a portion that constitutes an oil passage in an end surface contact state between only a portion of a transfer cylinder 38 and an input joint 39;

FIG. 4 is a perspective view showing a cut oil passage 2, an outer oil passage 7, and an inner oil passage 18 provided on an end face of a transfer cylinder 38.

FIG. 5 is a side view of the transfer cylinder 38;

6 shows a cut oil passage 2 and an outer oil passage 7 on the end face side of the transfer cylinder 38. FIG.
FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input shaft 2 Cut oil passage 3 Drilling oil passage 38 Inherited cylinder 39 Input joint 39a Butt end surface 42 Fixed side seal case

──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Akinobu Nagano 2-181-1, Inaji, Amagasaki-shi, Hyogo Inside Kanzaki High-Tech Koki Manufacturing Co., Ltd. No. 18-1 Inside Kanzaki High-class Koki Seisakusho Co., Ltd. (72) Inventor Takashi Maeda 2-181-1, Inaji, Amagasaki-shi, Hyogo Prefecture Inside Kanzaki High-class Koki Seisakusho Co., Ltd. (56) References 256927 (JP, A) JP-A-4-181060 (JP, A) JP-A-5-231524 (JP, A) JP-A-1-120439 (JP, A) Japanese Utility Model Application No. Sho 53-139449 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F16D 25/00-25/12

Claims (2)

(57) [Claims] 1. A transfer cylinder (38) and an input joint (39) are fixed to the outer periphery of an input shaft (1) having a radial oil passage (12) formed therein.
8 and the outer periphery of the input joint 39 are fitted with a fixed-side seal case 42, and from the fixed-side seal case 42 via the oil passage of the transfer cylinder 38 or the input joint 39, the radial oil inside the input shaft 1. In the configuration in which the pressure oil is supplied to the passage 12, the transfer cylinder 38
And the cut oil passage 2 at one of the butting portions of the input joint 39.
And the cut oil passage 2 is closed at the end face of the input joint 39.
Constitutes an inherited oil passage, and a butt portion of the inherited cylinder 38
Is provided with an outer peripheral oil passage 7 communicating with the cut oil passage 2
And is formed in the outer peripheral oil passage 7 and the fixed side seal case 42.
With the perforated oil passage 17,
An inner oil passage 1 communicating with the cut oil passage 2 is provided on an inner periphery of the joining portion.
8 and was drilled in the inner peripheral oil passage 18 and the input shaft 1.
An oil passage structure of a pressure oil receiving portion, wherein the oil passage structure communicates with the radial oil passage 12 . 2. An oil passage structure of a pressure oil receiving portion according to claim 1.
Here, the input joint 39 is fitted on the outer periphery of the input shaft 1 on the opposite side.
Oil passage for supplying lubricating oil to the mounted roller bearing 21
4 is drilled in the transfer cylinder 38 as a drill hole from the cut oil passage 2
The end of the lubricating oil passage 4 on the roller bearing 21 side is throttled.
An oil passage structure of a pressure oil inheriting portion, wherein the oil passage structure has a hole 4a .