JP3164948B2 - Reversible hydraulic clutch mechanism for marine engines - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a reversible hydraulic clutch mechanism for a marine engine for switching the rotation of an engine mounted on a ship between forward and reverse.

[0002]

2. Description of the Related Art Heretofore, a technique relating to a reversible rotary hydraulic clutch mechanism of a marine engine has been known. For example, Japanese Utility Model Laid-Open No. 59-11943 and Japanese Utility Model Laid-Open No.
Such techniques are described in 108035 and JP-A-63-43048. Further, as a technique for interposing a vibration isolating elastic body at a connection portion between a flywheel and an input shaft of the marine engine, a technique as disclosed in Japanese Utility Model Publication No. 4-7382 is known.

[0003]

SUMMARY OF THE INVENTION The present invention relates to an inspection of a vibration-proof elastic body when a vibration-proof elastic body interposed between a flywheel of the engine and an input shaft for cushioning an impact is loosened. In order to facilitate repair and replacement, a rubber block ring is arranged inside the flywheel so that the flywheel and the rubber block ring are overlapped so that the length of the reversible hydraulic clutch mechanism of the marine engine does not become long. In addition, the inspection and replacement of the vibration isolating elastic body is facilitated.

[0004]

Means for Solving the Problems The present invention is configured as follows to solve the above-mentioned problems. That is, claim 1
According to this, in order to connect the input shaft 1 of the hydraulic clutch mechanism to the flywheel 37 of the engine, the flywheel 37 is
The rubber block ring 10 is fitted and fixed on the rear surface of the rubber block ring 10, and the vibration-proof elastic body 4 is fitted into the fitting hole 10 a of the rubber block ring 10.
4 and the engagement protrusion 9a of the rubber block spider 9 is fitted in the fitting groove 44a of the vibration-proof elastic body 44, with the rubber block spider 9 and the vibration-proof elastic body 44 remaining. The rubber block ring 10 can be pulled out rearward, and a takeout notch 37a is formed in a part of the flywheel 37, and the rubber block spider 9 is formed.
Is rotated to the position of the cutout portion 37a, and the vibration-proof elastic body 4
4 is detachable.

According to the second aspect, the rubber block spider 9 is fixed to the rear surface of the input joint 39 fixed to the input shaft 1, the rubber block spider 9 is removed from the input joint 39, and the rubber block spider 9 is fixed together with the vibration-proof elastic body 44. Flywheel 37
From the rear.

According to the third aspect, in the configuration in which the output shaft 2 which is supported on the same axis as the input shaft 1 so as to be rotatable differently is supported on the clutch case 50, the bearing of the output shaft 2 is provided at the front part. The small-diameter conical roller bearing 48 and the large-diameter conical roller bearing 49 at the rear constitute a double-row conical roller bearing.

[0007]

Next, the operation will be described. That is, according to the first aspect, by pulling out either the rubber block ring 10 or the rubber block spider 9 rearward, the vibration-proof elastic body 44 can be released in a detachable state. By lifting the reversible hydraulic clutch mechanism and moving it backward, or by lifting the engine or flywheel 37 and moving it forward,
Need not be released, and inspection and repair are simplified.

Further, by drawing rubber block ring 10 rearward, the vibration damping elastic member 44 and the rubber block spider 9 free to be rotatable relative to the flywheel 37, further extraction to flywheel 37 Since the notch 37a is provided, the vibration-proof elastic body 44 at a position facing the position of the takeout notch 37a can be removed and replaced with a new one.

According to the second aspect , the rubber vibration isolator 44 between the rubber block ring 10 and the rubber block spider 9 is released only by detaching the rubber block spider 9 from the input joint 39 and retracting the rubber block spider 9 rearward. Can be
The inspection and replacement of the vibration isolating elastic body 44 can be easily performed.

According to the third aspect of the present invention, conventionally, the forward load is calculated, and the conical roller bearing 49 which receives the rear forward load is calculated.
The conical roller bearing that determines the size of the front side and receives the reverse load on the front side uses the same size as the one for the forward movement of the rear part, but the load at the time of reverse movement is small and the frequency of use is small, so the small diameter Thus, a small conical roller bearing 48 can be used. In addition, the space for projecting the small-diameter conical roller bearing 48 inside the clutch case 50 is reduced, so that the overall length can be reduced.

[0011]

Next, an embodiment will be described. FIG. 1 is an overall side sectional view of a reversible hydraulic clutch mechanism of a marine engine according to the present invention, FIG. 2 is an enlarged sectional view of a forward hydraulic clutch device, a reverse hydraulic clutch device, and a planetary gear type reverse rotation mechanism, and FIG . A of 2
FIG. 4 is an enlarged sectional view showing a configuration of a flywheel 37, a rubber block ring 10, and a rubber block spider 9. FIG. 5 is another embodiment of the rubber block ring 10 and the rubber block spider 9. FIG. 6 shows the case of the variable pitch propeller mechanism.
Only with the clutch mechanism, the oil supply tube 52 for variable pitch propeller
Illustrates the configuration obtained when a, 7 illustrates a configuration in which a variable pitch propeller for refueling tube 55 on the outside of the clutch case 50, FIG. 8 is external perspective view of a vibration damping elastic member 44,
9 is a cross-sectional view of the vibration isolating elastic body 44 attached to the rubber block spider 9, and FIG. 10 is a cross-sectional view of the inspection and repair window 50a and a portion of the hydraulic oil piping 80 to the reverse hydraulic clutch device. 11 is a sectional view taken along the line BB in FIG. 1, and FIG. 12 shows the carrier 8 as a front carrier 8c and a rear carrier 8d.
FIG. 13 is a side sectional view of a front carrier 8c and a rear carrier 8d, and FIG. 14 is a flywheel 3.
It is a rear view which shows the part of 7 and the extraction notch 37a.

Referring to FIG. 1, the overall structure of a reversible hydraulic clutch mechanism for a marine engine will be described. During transmission of power from the flywheel 37 of the engine to the output coupling 51, a forward hydraulic clutch device, a reverse hydraulic clutch device, and a planetary gear type reversing mechanism are arranged inside the clutch case 50. The forward hydraulic clutch device is arranged and configured on the outer periphery of the output shaft 2, 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
A planetary gear type reversing mechanism constituted by a carrier 8 and a pinion is arranged in series on the outer periphery of the rear portion of the output shaft 2 in parallel with the overlapping portion.

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. The rubber block spider 9 is interposed on the rubber block ring 10 via a vibration-proof elastic body 44 . By interposing an anti-vibration elastic body 44 between the rubber block ring 10 and the rubber block spider 9, an impact mitigation mechanism is configured. The rubber block spider 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. An input lid 42 is fitted around the transfer cylinder 38, and a lubricating oil path and a forward oil path are connected to the input lid 42 from a hydraulic pressure switching valve by piping. The oil passage and the oil passage of the transfer cylinder 38 are rotatably connected to each other.

The input shaft 1 and the output shaft 2 are
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 2, 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 2, a planetary gear type reversing mechanism constituted by a carrier 8 and a pinion is arranged in series with a parallel portion of the forward hydraulic clutch device and the reverse hydraulic clutch device. The planetary pinion 16 and the reverse rotation pinion 14 are pivotally supported by the planetary gear shaft 15 and the reverse rotation planetary gear shaft 45 provided on the carrier 8, and are mounted on the clutch case 50 in order to facilitate inspection, repair and replacement of these planetary gears. , Inspection lid 50a.

The output shaft 2 is first pivotally supported on 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. The output shaft 2
The output joint 5
1 is fixed. Conventionally, the forward load is calculated to determine the size of the conical roller bearing 49 that receives the rearward forward load, and the conical roller bearing that receives the forward reverse load has the same size as the rearward forward use. However, since the load at the time of reversing is small and the frequency of use is low, it is possible to use a small-sized conical roller bearing 48 as a small diameter. This also allows the clutch case 5
Since the space for projecting the portion of the small-diameter conical roller bearing 48 into the inside of the cylinder 0 is reduced, the overall length can be reduced.

Next, details of the flywheel 37 and the rubber block ring 10 will be described with reference to FIG. The rubber block ring 10 is fitted on the rear surface of the flywheel 37. The rubber block ring 1
A fitting hole 10a for fitting the vibration-proof elastic body 44 is formed in the inner diameter portion of the vibration-proof elastic body 44.
The engagement protrusion 9a of the rubber block spider 9 is fitted in a. Maintenance and inspection and replacement of the vibration isolating elastic body 44 are required, and only the rubber block ring 10 is moved rearward while the rubber block spider 9 is fixed to the input joint 39.
It can be pulled out along the axial direction . The rubber
Remove the lock ring 10 as shown at 10 'in FIG.
In this case, a guide bolt is used.

[0017] The flywheel the rubber block ring 10
By pulling out from the wheel 37, the rubber block spider 9 remains in the flywheel 37 with the vibration-proof elastic body 44 attached to the portion of the engagement projection 9a,
In the removal notch 37a provided in the flywheel 37 ,
It is possible to remove and replace the vibration-proof elastic body 44 on the engaging projection 9a located . In this configuration,
Since the rubber block ring 10 can be pulled out rearward, the rubber block spider 9 does not need to be detached from the input joint 39, and the rubber block spider 9 is fixed to the engine-side surface of the input joint 39.

First, a transfer cylinder 38 is fitted to the input shaft 1, and an input joint 39 is fitted and fixed to the front part by hydraulic fitting. An input cover 42 is fitted over the outer circumference of the transfer cylinder 38 and the input joint 39. The input lid 42 is integrated with the clutch case 50 and does not rotate with the input shaft 1 but between the transfer cylinder 38 rotating with the input shaft 1 and the input lid 42 and the forward oil passages 60 and 62. And the lubrication oil passages 61 and 63 are inherited. The lubricating oil passages 61 and 63 are configured by closing a groove oil passage formed on a joint surface between the transfer cylinder 38 and the input joint 39 at the joint surface.

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 the forward oil passages 60 and 62, the lubricating oil passages 61 and 63, and the reverse oil passage 65 via the switching control valve.

Next, referring to FIG. 2, a detailed configuration of the forward hydraulic clutch device, the reverse hydraulic clutch device, and the planetary gear type reverse rotation mechanism will be described. The input shaft 1 is formed in a flange shape, and a forward actuator 3 is fitted around an outer periphery of a portion pivotally supporting the front end of the output shaft 2 via a bearing 32 therein.
The forward actuator 3 is formed in a donut shape. In the cylinder constituted by the input shaft 1 and the forward actuator 3, the forward oil passage 6 of the transfer cylinder 38 is provided.
From 0.62, pressure oil is supplied through a forward oil passage 21 formed in the input shaft 1.

By projecting the forward actuator 3, the forward friction plate mechanism 6 is pressed and brought into contact with the input shaft 1.
The rotation of the forward clutch housing 11 integrated with
The power is transmitted to the forward friction plate locking ring 7. Since the forward friction plate engaging ring 7 is fixed to the output shaft 2 by hydraulic fitting, the rotation of the input shaft 1 is transmitted to the output shaft 2 via the forward friction plate mechanism 6. . An oil passage 27 formed in the output shaft 2 is an oil passage for hydraulically fitting the forward friction plate locking ring 7.

At the time of forward movement, power is transmitted from the input shaft 1 via the forward clutch housing 11 and the forward friction plate mechanism 6 by driving the forward friction plate locking ring 7 and the output shaft 2. At the time of reverse, the forward friction plate mechanism 6 is released, and the reverse friction plate mechanism 5 is pressed and joined by the reverse actuator 4. That is, the forward clutch housing cover 1 is attached to the forward clutch housing 11.
8 is fixed. The reverse drive gear 17 is integrated with the forward clutch housing cover 18.

The reverse drive gear 17 rotates integrally with the rotation of the input shaft 1. The planetary pinion 16 of the planetary gear shaft 15 meshes with the reverse drive gear 17. Planetary pinion 16 meshes always with reverse pinion 1 4 on the reverse planetary gear shaft 45. The reversing pinion 14 is
And the reverse driven gear 13 is meshed. When the forward friction plate mechanism 6 is joined and the reverse friction plate mechanism 5 is separated, the reverse drive gear 17 is engaged with the planetary pinion 16, the planetary pinion 16 is engaged with the reverse pinion 14, and the reverse Since the output shaft 2 of the drive gear 13 rotates forward, the reverse drive gear 17 and the reverse driven gear 13 have the same rotation direction , and neither the planetary pinion 16 nor the reverse pinion 14 rotates. Meanwhile, the carrier 8 is rotating in the same direction as the forward rotation of the output shaft 2.

In the case of reverse travel, when the forward friction plate mechanism 6 is separated and the reverse friction plate mechanism 5 is joined, the rotation of the input shaft 1 causes the forward clutch housing cover 18 to move from the forward clutch housing 11 to the forward clutch housing cover 18. Via the reverse drive gear 17
The reverse drive gear 17 rotates the planetary pinion 16. At this time, the carrier 8 is fixed to the reverse clutch housing 12 by the reverse friction plate mechanism 5, and the reverse clutch housing 12 is fixed to the clutch case 50, so that the carrier 8 cannot rotate. Since the carrier 8 does not revolve, the planetary gear shaft 15 and the reverse planetary gear shaft 45 do not revolve, start rotating, and forcibly rotate the reverse driven gear 13 in the reverse direction.

The reverse rotation to the output shaft 2 by the reverse rotation of the rear advancing the driven gear 13 is obtained. And in the present invention,
Since the reversing mechanism is constituted by a planetary gear type reversing mechanism, the reduction ratio of the reverse rotation to the rotation of the input shaft 1 can be changed by freely changing the design of the number of teeth of the planetary pinion 16 and the reverse rotation pinion 14. It is. The present invention, in order to slightly slow the reverse rotation than the forward rotation,
The reduction ratio is configured to be 1 or more. With this, when switching from forward to reverse, due to inertial navigation,
It is possible to solve the problem that an excessive load is applied to the propeller when the vehicle is moving backward and engine stall occurs. The reverse clutch housing 12 is fixed integrally with the clutch case 50, and the reverse clutch housing 1
Hydraulic oil is supplied to the reverse oil passage 65 provided in the pipe 2 by piping. The reverse actuator 4 is normally urged toward the separation side by a separation urging spring 36.

The reverse clutch housing 12 is covered with a reverse clutch housing cover 19 to prevent the reverse friction plate mechanism 5 from slipping out between the reverse clutch housing 12 and the cover 19. The inner diameter of the reverse friction plate mechanism 5 is locked to a portion of a reverse friction plate locking ring 8 a protruding from the carrier 8. By forming the reverse friction plate engaging ring 8a on the carrier 8, as in the present invention, the forward hydraulic clutch device and the reverse hydraulic clutch device can be arranged in parallel, and the planetary gear type reversing mechanism can be arranged in series. It is.

A bearing 33 is fitted on the outer periphery of the joint surface between the forward clutch housing cover 18 and the reverse drive gear 17, and the bearing 33 pivotally supports the front portion of the carrier 8. The rear part of the carrier 8 is pivotally supported by a bearing 34 fitted on the output shaft 2. The lubricating oil passages 61 and 63 of the input shaft 1
Thus, the oil is transferred from the lubricating oil passage 22 of the output shaft 2 via the oil passage 23 to the oil of the carrier 8 via the lubricating oil passage 66 of the input shaft 1 and the pivoting portion between the input shaft 1 and the output shaft 2. Passed to Road 24. From the oil passage 24 of the carrier 8, the oil passages 25 and 68 in the planetary gear shaft 15 and the reverse planetary gear shaft 45, and the oil passages 26 and 47 in the portion of the reverse side friction plate locking ring 8a.
It is guided to. From the oil passage 26, the reverse friction plate mechanism 5
The lubricating oil is discharged to the inner diameter part of.

An oil passage 35 formed in the output shaft 2 shown in FIG.
The lubricating oil is discharged to the inner diameter portion of the forward friction plate mechanism 6 through the oil passage 67 of the forward friction plate locking ring 7 to lubricate the forward friction plate mechanism 6. The lubricating oil from the oil passage 67 passes through the oil passage 29 of the forward clutch housing 11,
The lubricant is ejected with the rotation of the forward clutch housing 11, and the lubricating oil reaches inside the reverse friction plate engaging ring 8a. The lubricating oil on this path also lubricates the reverse friction plate mechanism 5.

Next, the configuration of the carrier 8 will be described with reference to FIG. The carrier 8 is integrally connected to the front and rear portions by a connecting portion 8b, between which the planetary pinion 16 and the planetary gear shaft 15 and the reverse rotation pinion 14 and the reverse rotation planetary gear shaft 4 are connected.
5 is a set to support the bearing. By integrating the carrier 8 in this way, the size of the carrier 8 can be reduced.

In FIG. 5, a rubber block ring 1
FIG. 2 illustrates another mechanism of the rubber block spider 9 and the rubber block spider 9. In FIG. 4, the rubber block ring 10 can be pulled out. In FIG. 5, the rubber block spider 9 is fixed to the rear surface of the input joint 39 by bolts, and the rubber block spider 9 is removed. It can be retracted backward along the axial direction . Then , as shown at 9 ' , when the rubber block spider 9 is lowered backward , the rubber block spider 9 can be taken out with the vibration-proof elastic body 44 attached to the engagement projection 9a. Can be exchanged. With this configuration, the vibration isolating elastic body 4
This eliminates the need to lift the clutch case 50 with a crane and move the engine and flywheel 37 forward when inspecting and replacing 4.

The variable pitch propeller mechanism is a mechanism that can switch between forward and reverse by changing the propeller angle. In this case, there is no need to provide a reverse hydraulic clutch device inside the clutch case 50. . In the present invention, when such a variable pitch propeller mechanism is provided, only the forward hydraulic clutch device is left, and the reverse hydraulic clutch device and the planetary gear type reverse rotation mechanism are removed while the same clutch case 50 is provided. Te, it is possible to arrange the fuel supply tube 52 for variable pitch propeller at the rear of the clutch case 50. In the case of Figure 7, than it is necessary to provide a variable pitch propeller for refueling tube 55 in the portion of the propeller shaft connected to the output coupling 51.

FIG. 10 shows a portion in which the hydraulic oil piping 80 is communicated toward the reverse oil passage 65 for the reverse hydraulic clutch device. The pressure oil piping 80
Is formed integrally with the lid 82, and the external pressure oil piping 81 communicates with the lid 82. Therefore, by removing the lid 82, the internal pressure oil piping 80 is removed.
Can be removed at the same time. As shown in FIG. 11, the reverse clutch housing 12 is provided with a mounting surface 5 provided on the side of the lower case 50c at the joint surface between the upper case 50b of the clutch case 50 and the lower case 50c.
0d, and is fixed by fixing bolts 88.

As shown in FIGS. 12 and 13, the carrier 8 is constituted as a separate body of a front carrier 8c and a rear carrier 8d, and a connecting body is provided between the separate front carrier 8c and the rear carrier 8d. The carrier 8 can be connected to form the carrier 8 integrally. In FIG. 14, the flywheel 37 for the embodiment of FIG.
The relative position between the takeout notch 37a and the vibration-proof elastic body 44 is shown. Rubber block ring 10
When removed from the wheel 37, the upper part of the vibration-proof elastic body 44
Since it is opened, insert your hand into the
From this , removal of the rubber block ring 10 can be facilitated.

[0034]

As described above, the present invention has the following advantages. That is, since the rubber block ring 10 or the rubber block spider 9 is pulled out rearward, the vibration-proof elastic body 44 can be released in a detachable state. As described above, there is no need to lift the reversible rotary hydraulic clutch mechanism and move it backward, or lift the engine or flywheel 37 and move it forward to release the vibration isolating elastic body 44, which makes inspection and repair easy. It becomes. Further, by pulling out the rubber block ring 10 backward, the vibration isolating elastic body 44 and the rubber block spider 9 can be freely rotatable with respect to the flywheel 37. Further, the takeout notch 37a is formed in the flywheel 37. Is provided, the anti-vibration elastic body 44 at the position facing the position of the extraction notch 37a can be removed and replaced with a new one.

The rubber block spider 9 is fixed to the rear surface of the input joint 39 fixed to the input shaft 1, and the rubber block spider 9 is fixed to the input joint 39.
And the rubber block spider 9 can be pulled out rearward from the flywheel 37 together with the vibration-proof elastic body 44. Therefore, the rubber block spider 9 can be removed from the input joint 39 and retracted rearward, and the rubber block ring 10 and the rubber block spider 9 can be removed. Can release the vibration isolating elastic body 44 between
Inspection and replacement of the vibration isolating elastic body 44 can be easily performed.

According to a third aspect of the present invention, the output shaft 2 supported on the same axis as the input shaft 1 so as to be rotatable differently from the input shaft 1 is connected to the clutch case 5.
0, the output shaft 2 has a front small-diameter conical roller bearing 48 and a rear large-diameter conical roller bearing 4.
9, the load at the time of forward movement is conventionally calculated to determine the size of the conical roller bearing 49 which receives the rearward forward load, and the conical roller which receives the forward reverse load is conventionally formed. The bearing used was the same size as that used for the forward movement of the rear part.However, since the load at the time of backward movement is small and the frequency of use is low, it is possible to use a small one as the small diameter conical roller bearing 48. It has become. In addition, since the space for projecting the small-diameter conical roller bearing 48 inside the clutch case 50 is reduced, the overall length can be reduced.

[Brief description of the drawings]

FIG. 1 is an overall side sectional view of a reversible rotary hydraulic clutch mechanism for a marine engine according to the present invention.

FIG. 2 is an enlarged sectional view of a forward hydraulic clutch device, a reverse hydraulic clutch device, and a planetary gear type reverse rotation mechanism.

FIG. 3 is a sectional view taken along the line AA of FIG . 2 ;

FIG. 4 Flywheel 37 and rubber block ring 1
FIG. 2 is an enlarged cross-sectional view showing a configuration of a part including a rubber block spider 9 and a part 0.

FIG. 5 is a drawing showing another embodiment of the rubber block ring 10 and the rubber block spider 9.

In the case of FIG. 6 variable pitch propeller mechanism, it illustrates only the clutch mechanism, the configuration obtained when a refueling tube 52 for variable pitch propeller.

[7] illustrates a structure in which a variable pitch propeller for refueling tube 55 on the outside of the clutch case 50.

8 is an external perspective view of the vibration-proof elastic body 44. FIG.

FIG. 9 shows a state of being attached to a rubber block spider 9 .
Sectional drawing of the vibration-proof elastic body 44 of FIG.

FIG. 10 is a cross-sectional view of an inspection and repair window 50a and a portion of hydraulic oil piping 80 to a reverse hydraulic clutch device.

FIG. 11 is a sectional view taken along a line BB in FIG. 1;

FIG. 12 is a front sectional view of an embodiment in which the carrier 8 is divided into a front carrier 8c and a rear carrier 8d and integrated by a connecting body 83.

FIG. 13 is a side sectional view of a front carrier 8c and a rear carrier 8d.

FIG. 14 is a rear view showing a flywheel 37 and an extraction notch 37a.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Input shaft 2 Output shaft 5 Reverse friction plate structure 6 Forward friction plate structure 8 Carrier 9 Rubber block spider 10 Rubber block ring

──────────────────────────────────────────────────続 き Continuing from the front page (72) Inventor Takashi Maeda 2--18-1, Inaji, Amagasaki-shi, Hyogo Prefecture Inside Kanzaki High-Tech Koki Mfg. Co., Ltd. (72) Inventor Kubo 1-32 Chayamachi Yanmar Diesel Co., Ltd. (72) Inventor Kobo Mizuno 1-32 Chayacho Kita-ku, Osaka City, Osaka Prefecture Yanmar Diesel Co., Ltd. (56) References JP-A-3-295792 (JP) JP-A-60-237248 (JP, A) JP-A-5-215145 (JP, A) JP-A-60-162737 (JP, U) JP-A-59-94632 (JP, U) (58) Field surveyed (Int.Cl. ⁷ , DB name) F16F 15/10-15/36 B63H 23/08 B63H 23/30

Claims (3)

(57) [Claims] 1. A rubber block ring 10 is fitted and fixed to a rear surface of a flywheel 37 to connect an input shaft 1 of a hydraulic clutch mechanism to a flywheel 37 of an engine.
The vibration-proof elastic body 44 is fitted into the fitting hole 10a of the rubber block ring 10, and the fitting groove 44a of the vibration-proof elastic body 44 is
In a configuration in which the engagement protrusion 9a of the rubber block spider 9 is fitted, the rubber block ring 10 can be pulled out rearward with the rubber block spider 9 and the vibration isolating elastic body 44 left, and a part of the flywheel 37 is formed. A reciprocating hydraulic system of a marine engine, characterized in that a cutout notch 37a is formed in the rubber engine, and the rubber block spider 9 is rotated to the position of the cutout notch 37a so that the vibration-proof elastic body 44 can be detached. Clutch mechanism. 2. The reversible rotary hydraulic system for a marine engine according to claim 1.
In the clutch mechanism, the rubber block spider 9
Is fixed to the rear surface of the input joint 39 fixed to the input shaft 1,
A reversible hydraulic clutch mechanism for a marine engine, wherein the rubber block spider 9 is detached from the input joint 39 so that the rubber block spider 9 can be pulled out from the flywheel 37 together with the vibration-proof elastic body 44. 3. In a configuration in which an output shaft 2, which is supported on the same axis as the input shaft 1 so as to be rotatable differently, is supported on a clutch case 50, the output shaft 2 is provided with a front small-diameter conical roller bearing 48. And a large-diameter conical roller bearing 49 at the rear, and a double-row conical roller bearing.