JPH0134989Y2 - - Google Patents

Description

[Detailed Description of the Invention] (a) Field of Industrial Application The present invention relates to a lubricating device for a hydraulic clutch device in a hydraulic clutch type transmission.

(b) Prior art and its problems When not connected to the hydraulic clutch device, the friction plate and facing rotate in a state close to contact, and when proper lubrication is lost, rotation occurs and the neutral position cannot be achieved. Otherwise, the hydraulic clutch device always seemed to be dragging other hydraulic clutch devices, resulting in a waste of transmitted power.

To solve this problem, lubricating oil that constantly lubricates each hydraulic clutch device is sent through the seal case and the hydraulic clutch shaft, but conventionally, lubricating oil passages leading to each seal case were provided separately. Therefore, a number of oil passages were constructed by bypassing the outer periphery of other seal cases.

Therefore, the structure of the oil passage becomes complicated and the oil passage plate becomes large.

The present invention solves the above-mentioned problems.

(c) Means for solving the problem The purpose of the present invention is as described above, and the configuration for achieving the purpose will be explained below.

The ends of the hydraulic clutch shafts 27, 28, 29, which are suspended horizontally on the transmission case 2, are connected to the transmission case 2.
In the configuration, the seal cases 42, 43, 44 of the oil passage plate 41 protrude outward and cover the protrusion with the seal cases 42, 43, 44 via the oil passage plate 41.
The insertion holes are made larger in diameter than the outer diameter of the seal case insertion part to form annular oil passages l ₃ , l ₅ , l ₇ , and the annular oil passages l ₃ ,
l ₅ and l ₇ are communicated with the lubricating oil passages l ₉ and l ₁₁ of the hydraulic clutch device via the respective seal cases 42, 43, and 44, and an oil passage l is connected between the transmission case 2 and the oil passage plate 41. ₂ , _l4 , _l6 , the oil passage _l2 extends from an appropriate position of the annular oil passage _l3 to connect to the oil passage _l1 for lubricating oil supply, and the oil passage _l4 , l ₆ are formed extending from appropriate positions of the annular oil passages l ₃ , l ₅ , l ₇ to connect adjacent annular oil passages.

(d) Embodiment The purpose of the present invention is as described above, and the structure of the present invention will be explained based on the structure of the embodiment shown in the attached drawings.

Fig. 1 is a rear sectional view showing a hydraulic clutch type transmission, Fig. 2 is a drawing showing another embodiment of the steering clutch and brake section, Fig. 3 is an enlarged view of Fig. 1, and Fig. 4 is a hydraulic Drawing showing the oil passage on the side of the clutch type transmission, Fig. 5 is a plan sectional view of the transmission hydraulic valve, Fig. 6 is a plan view showing the oil passage of the day relief valve section, and Fig. 7 is the transmission hydraulic valve. FIG. 3 is a side cross-sectional view of the day-relief valve.

In FIGS. 1, 2, and 3, rotation from the engine is transmitted to the input shaft 1. In FIG. The input shaft 1 protrudes from the right side of the transmission case 2, and a dual hydraulic pump device is fixed to the end of the input shaft 1 which protrudes through the left side. The hydraulic pump 4 is a hydraulic pump for a hydraulic clutch type transmission, and the hydraulic pump 3 is a hydraulic pump for a hydraulic brake.

A transmission hydraulic valve V and a day-relief valve device are placed on the upper surface of the transmission case 2.

A loose gear 5 on the input shaft and a fixed gear 8 on the shaft 26
are always in mesh with each other, and the loosely fitted gear 7b on the input shaft 1 and the shaft 2
The fixed gear 10 on top of 6 is also always in mesh. By sliding the sliding gears 6b and 6a on the input shaft in eight stages, the fixed gears 8, 9, and 10 on the shaft 26 are selectively engaged, and high, middle, and low sub-shifts can be obtained.

Fixed gears 8, 11 on shaft 26 and loose gears 13, 14 of hydraulic clutch devices 16, 17 on shaft 27
are always engaged.

When the hydraulic clutch devices 16 and 17 are selectively engaged by operating the shift hydraulic valve, H speed rotation is obtained by the engagement of the hydraulic clutch device 16.
By engaging the hydraulic clutch device 17, L speed rotation is obtained. That is, when the hydraulic clutch device 17 is in the engaged state, when the hydraulic clutch device 18 is next engaged.
F2 speed, F1 speed when 19 is engaged, R1 when 20 is engaged
Becomes faster.

Also, when the hydraulic clutch device 16 is in the engaged state, when the hydraulic clutch device 18 is next engaged, F4 speed, 19
Combining 20 will give you F3 speed, and combining 20 will give you R2 speed.

Therefore, it is necessary to first selectively engage one of the hydraulic clutch devices 16, 17 and then selectively engage one of the hydraulic clutch devices 18, 19, 20 by moving the shift lever, so the shift hydraulic valve does not have a spool. 51 and 50 are arranged in parallel and slide together as one.

The spool 51 selectively engages the hydraulic clutches 16, 17, and the spool 50 selectively engages the hydraulic clutches 18, 19, 20.

The loosely fitted gears 13, 14, 21, 23, and 25 are arranged to enable the above speed change. The small diameter gear 22 sandwiched between the hydraulic clutch devices 18 and 19 on the shaft 28 and the small diameter gear 24 on the shaft 29 are both connected to the shaft 30.
It meshes with the upper large diameter gear 33.

As shown in FIG. 4, the shafts 27, 28, 29 are
6, and the shafts 28, 29
is located at the base of an isosceles triangle with axis 30 as its apex.

A hydraulic clutch device 20 is disposed on the left and right half of the shaft 29, and a parking brake device A is disposed protrudingly on the right half.

The parking brake device A consists of a brake arm 38, a brake drum 39, and a brake shoe.
Previously, it protruded from the mission case wall, but
In this case, it is inserted into the transmission case 2. On the shaft 30 are left and right clutch gears 34L, 3.
4R and brake friction plates 40L, 40R are integrally constructed, and the shifter fork 48L, 4 shown in FIG.
8R allows the steering brake to be applied in conjunction with turning the steering clutch on and off. Shifter fork 48L, 48R has arms 47L, 47
It is operated by the piston of the brake cylinder 45 via the link R and constitutes a hydraulic brake device. 46 is an electromagnetic valve for operating the hydraulic brake. The clutch gears 34L, 34R drive the drive sprocket shafts 32L, 32R of the crawler type traveling device via fixed gears 35L, 35R, shafts 31L, 31R, and reduction gears 36, 37.

The transmission case 2 is composed of a split transmission case, and an oil passage plate 41 is further attached to the outer surface of the left side transmission case. ,44
has been fixed.

An oil passage is formed on the mating surface between the outer wall of the transmission case 2 and the oil passage plate 41, and oil is supplied to each hydraulic crawler device through this oil passage.

To explain the path of pressure oil from FIG. 4, FIG. 5, FIG. 6, and FIG. 7, the discharge side oil path PS ₁ of the hydraulic pump 4
From there, it passes through oil road PS ₃ and enters oil road PS ₂ . It exits to the oil passage PS ₄ of the valve case 61 shown in FIG. 5 and enters the oil passage PS ₅ of the day relief valve case 62 shown in FIG. Throttle valve 5 of the day relief valve from PS ₆
8 into the oil passage PS ₇ , and the other side leads to the oil passage PS ₈ .

As shown in Figure 5, oil passage PS ₈ is the valve spool 51.
PS ₁₁ communicates with the oil passage PS ₁₁ of the spool 50, and oil passage PS ₁₂ of the spool 50 also communicates with PS ₉ . In FIG. 6, PS ₉ communicates with PS ₁₀ , from which it enters the spool 55 of the day relief valve. The day relief valve serves to delay the rising curve of the hydraulic pressure in order to avoid sudden engagement of the hydraulic clutch device when starting the vehicle, and after the hydraulic clutch device is engaged, it continues to discharge pressure oil like a normal relief valve.

In the present invention, the pressure oil spouted from the spool 55 of the day relief valve is used to lubricate the hydraulic clutch device through oil passages _l12 and _l13 and _l14 .

First, to explain the movement of the spool 55 of the day relief valve, the spool of the valve moves,
When pressure oil flows into the hydraulic clutch device and the pressure starts to rise, the pressure oil enters the notch 55b of the spool 55 from the oil passage PS ₁₀ , enters the back chamber from the throttle oil passage 55a, and pushes the spool 55 to the right to release the pressure oil. I made the drain oil path _l12 communicate with _PS10 , and the pressure oil is _l12 , _l13 ,
l ₁₄ and the lubricating oil passage, and the pressure in the hydraulic clutch device does not increase. Next, the spring 56 is pushed to the left from the pressure oil passage PS ₇ through the throttle valve 58 to push back the spool 55 and suppress the spouting of pressure oil to the drain circuit, causing the pressure oil curve of the hydraulic clutch device to rise. I am going.

Next, the movement of the spools 50 and 51 and the movement of pressure oil for gear shifting will be explained.

Figure 5 shows the state of R2 speed. Spool 51
In this case, the pressure oil of PS ₁₁ enters the _H4 oil passage through the penetrating oil passage a, and the _H4 oil passage connects the hydraulic clutch device 16 from the _H1 oil passage in Fig. 4 through the _H2 and _H3 oil passages. . On the other hand, in the spool 50, the pressure oil of PS ₁₂ enters the _r4 passage from the through oil passage c, and the hydraulic clutch device 20 is connected through the oil passages r ₁ , r ₂ , r ₃ in Fig. 4, and the R2 speed is adjusted. It is becoming.

Next, at R1 speed, the spool 51 is moved from the through oil passage b.
Enters the L ₄ oil passage, and the L ₄ oil passage is connected to L 6 and L 9 via L _{7 and} L ₈ in Fig. 6, and L ₉ is connected to L ₁ and L ₉ in Fig. 4.
The oil enters the hydraulic clutch device 17 from the L ₂ and L ₃ oil passages and is connected. The spool 50 has a penetrating oil passage c from PS ₁₂ .
to _R4 , and also connects the hydraulic clutch device 20 to obtain R1 speed.

In the N state, PS ₁₁ of spool 51 is through oil passage b
This leads to drain oil line l ₁₈ . In the spool 50, the PS ₁₂ communicates with the drain oil passage l ₁₇ through a through oil passage f.

At F1 speed, the PS ₁₁ oil passage of the spool 51 communicates with L ₅ through oil passage b, and is connected to the hydraulic clutch device 17 through L ₇ , L ₈ , L ₆ , and L ₉ . Spool 50
The PS ₁₂ enters the _S4 oil passage and enters the hydraulic clutch device 19 from the S ₁ , S ₂ , and S ₃ oil passages in FIG.

At F2 speed, the PS ₁₁ oil passage of the spool 51 enters L ₆ through the through oil passage b, coupling the hydraulic clutch device 17, and the PS ₁₂ oil passage of the spool 50 enters the M ₄ oil passage as shown in _FIG. , M ₂ , and M ₃ to connect the hydraulic clutch device 18 .

At F3 speed, the PS ₁₁ oil passage of spool 51 enters the H ₄ oil passage to engage the hydraulic clutch device 16, and the PS ₁₂ oil passage of spool 50 enters the S ₄ oil passage to engage the hydraulic clutch device 19.

At F4 speed, the PS ₁₁ oil passage of spool 51 communicates with the H ₄ oil passage, coupling the hydraulic clutch device 16, and the PS ₁₂ oil passage of spool 50 enters the M ₄ oil passage, coupling the hydraulic clutch device 18.

To explain the drain oil and lubricating oil passages for lubricating the hydraulic clutch device, as mentioned above, the drain oil passage _l12 of the day relief valve connects to the oil passage _l16 of the valve case 61 via _l13 and _l14 . It enters, merges with the drain oil passage _l17 of the spool 50, further merges with the drain oil passage _l18 of the spool 51, and leads from the oil passage _l21 to the _l1 oil passage in FIG. 4. Oil passage l ₁ enters oil passage l ₃ on the outer periphery of shaft 29 from oil passage l ₂ , then oil passage l ₆ of shaft 28 from oil passage l ₄ , and oil passage l ₇ of shaft 27 from oil passage l ₆ . It also communicates with The outer peripheral oil passages of these shafts l ₃ ,
l ₅ , l ₇ are oil passages l ₈ , l ₁₀ on the transmission case side of seal cases 42, 43, 44 from shafts 27, 28, 2.
9, the hydraulic clutch device 16,
The hydraulic clutch device is constantly lubricated by lubricating oil passages l ₉ and l ₁₁ of 17, 18, 19, and 20.

This is because, regardless of the gear position, as long as the hydraulic pump 4 is rotating, lubrication is performed by the pressure oil spouted from the day relief valve.

Pressure oil for the hydraulic brake system is discharged from the hydraulic pump 3 through oil passages PB ₁ and PB ₂ shown in FIG. 4 to PB ₆ shown in FIG. 5. Next, from PB ₇ in Figure 6 to PB ₈ and PB ₉ ,
It also appears in PB ₃ in Figure 4. PB ₄ from PB ₃ , PB ₅
It enters the hydraulic cylinder 45 and electromagnetic valve 46 through the.

Reference numerals 59 and 59 in FIG. 7 are detent balls that simultaneously regulate the movements of the spools 50 and 51. Fifth
As shown in the figure, the arm 5 is
2 rotates, simultaneously sliding the spools 50 and 51, and four forward speeds and two reverse speeds can be obtained by rotating the speed change lever in one direction.

In the overall configuration as described above, the present invention relates to the lubricating oil passages to the shafts 27, 28, 29 on which the hydraulic clutch devices are mounted.

That is, the oil passage plate 4 is installed on the left side of the transmission case 2.
1, and the shaft 2 of the hydraulic clutch is attached to the oil passage plate 41.
Seal cases 42, 4 that cover the ends of 7, 28, 29
Open seal case insertion holes with a slightly larger diameter than the boss portions of seal cases 42, 43, and 44.
Doughnut-shaped annular oil passages l ₇ , l ₅ , and l ₃ are formed between the outer periphery of the boss part and the seal case insertion hole.

Then, the lubricating oil that is the confluence of the drain oil and the relief discharge oil is guided from the oil passage _l1 , which is the supply port, to an appropriate position in the donut-shaped annular oil passage _l3 through the oil passage _l2 ,
An oil passage _l4 formed to extend from an appropriate position of the annular oil passage _l3
The oil is guided to an annular oil passage _l5 at the annular oil passage l5, and is led to an annular oil passage _l7 at an oil passage _l6 extending from an appropriate position of the annular oil passage _l5 .

This results in donut-shaped annular oil passages l ₇ , l ₅ , l ₃
The oil passages L ₆ , L ₄ , and L ₂ are arranged in a chain.

Furthermore, oil passages formed from the annular oil passages l ₇ , l ₅ , l ₃ to the boss portions of the seal cases 42 , 43 , 44
communicates with lubricating oil passages l ₉ and l ₁₁ via l ₈ , l ₁₀ , l ₁₂ and further through oil passages bored in the axes of shafts 27, 28, 2;
It is designed to lubricate the hydraulic clutch system.

(E) Effects of the invention As constructed as described above, the invention has the following effects.

First, since an annular oil passage is provided around each seal case, it is now possible to freely select the communication position for communicating each oil passage.

Second, the communicating oil passages are straight and do not require frequent detours, and each annular oil passage can be connected with a single oil passage, so the oil passage can be simplified and the oil passage plate It became possible to make it smaller.

Thirdly, since the oil sent to the annular oil passage is a lubricating oil, even if the annular oil passage is poorly sealed, there is no problem with the operation of the clutch, etc.

[Brief explanation of the drawing]

Fig. 1 is a rear sectional view showing a hydraulic clutch type transmission, Fig. 2 is a drawing showing another embodiment of the steering clutch and brake section, Fig. 3 is an enlarged view of Fig. 1, and Fig. 4 is a hydraulic Drawing showing the oil passage on the side of the clutch type transmission, Fig. 5 is a plan sectional view of the transmission hydraulic valve, Fig. 6 is a plan view showing the oil passage of the day relief valve section, and Fig. 7 is the transmission hydraulic valve. FIG. 3 is a side cross-sectional view of the day-relief valve. l ₁ , l ₂ , l ₄ , l ₆ ... oil path, l ₃ , l ₅ , l ₇ ... annular oil path, l ₉ , l ₁₁ ... lubricating oil path, 2... transmission case, 41... ...Oil road plate, 42, 43, 44... Seal case, 27, 28, 29... Shaft on which a hydraulic clutch device is installed.

Claims (1)

[Scope of utility model registration request] The ends of the hydraulic clutch shafts 27, 28, 29, which are suspended horizontally on the transmission case 2, are connected to the transmission case 2.
In the configuration, the seal cases 42, 43, 44 of the oil passage plate 41 protrude outward and cover the protrusion with the seal cases 42, 43, 44 via the oil passage plate 41.
The insertion holes are made larger in diameter than the outer diameter of the seal case insertion part to form annular oil passages l ₃ , l ₅ , l ₇ , and the annular oil passages l ₃ ,
l ₅ and l ₇ are communicated with the lubricating oil passages l ₉ and l ₁₁ of the hydraulic clutch device via the respective seal cases 42, 43, and 44, and an oil passage l is connected between the transmission case 2 and the oil passage plate 41. ₂ , _l4 , and _l6 , the oil passage _l2 is extended from an appropriate position of the annular oil passage _l3 and connected to the lubricating oil supply oil passage _l1 , and the oil passage _l4 , l ₆ is formed to extend from appropriate positions of the annular oil passages l ₃ , l ₅ , and l ₇ to connect adjacent annular oil passages.