WO2014157978A1

WO2014157978A1 - Wet hydraulic multi-plate clutch

Info

Publication number: WO2014157978A1
Application number: PCT/KR2014/002646
Authority: WO
Inventors: 신기성
Original assignee: 대동공업 주식회사
Priority date: 2013-03-28
Filing date: 2014-03-28
Publication date: 2014-10-02
Also published as: KR20140118247A; KR101989183B1

Abstract

A wet hydraulic multi-plate clutch is disclosed. The wet hydraulic multi-plate clutch according to the present invention comprises a clutch housing and a hub gear capable of freely rotating with regard to the clutch housing. Multiple clutch plates and clutch disks are positioned alternately and spline-coupled to the inner diameter surface of the clutch housing and to the outer diameter surface of the hub gear. A piston is installed inside the clutch housing. A return spring is installed in front of the piston. Channels are formed in a hollow shaft, the piston, the hub gear, and the clutch housing, thereby allowing oil to flow from the hollow shaft to the outside of the clutch housing. A pressure plate is assembled near an opening of the clutch housing via a snap ring in a constrained manner. An oil seal is installed on the outer diameter surface of the hub gear, which faces the inner end of the pressure plate. At least one contact protrusion is formed on the outer diameter surface of the oil seal to make contact with the inner end of the pressure plate.

Description

Wet Hydraulic Multiplate Clutch

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hydraulically actuated multi-plate clutch, and more particularly, to a wet multi-plate clutch in which the clutch is filled with oil and smooth clutch regulation is performed by the filled oil and frictional heat is absorbed.

Agricultural trucks such as tractors, which are mainly used for farming, are frequently shifted from low speed to high speed or from high speed to low speed, from forward to reverse, or from reverse to forward, and the power output from the engine Shuttle transmission devices are employed for conversion to power with suitable speed and direction.

Shuttle transmissions employed in conventional agricultural work vehicles generally have a synchronized clutch on a shuttle shaft that is electrically connected to an engine output shaft, and alternatively to a shuttle gear on the shuttle shaft by operation of the clutch. It has a mechanical structure including engaging forward / reverse gears and interlocking with a clutch in conjunction with the operation of a shift lever.

However, the mechanical structure has a problem that the operation is inconvenient because the mechanical structure is bulky, the noise is high due to the connection between the gears during the shift, and the shift is entirely performed by the driver's operation force. Therefore, in recent years, as in automobiles, hydraulic shifts are assisted by hydraulic shifts, so that the shift is realized without a large force.

1 is a schematic cross-sectional view schematically showing an internal configuration of a conventional hydraulic transmission device for a farm vehicle having a configuration in which shifting is performed by hydraulic pressure. With reference to this it will be briefly described the configuration of the conventional hydraulic transmission.

As shown in FIG. 1, the conventional hydraulic transmission includes a shuttle shaft 100 directly connected to the engine output shaft, a transmission shaft 200 parallel to the shuttle shaft 100, and a traveling output shaft 300 freely rotatable on the shuttle shaft. The shuttle shaft 100 is provided with a pair of left and right shuttle clutches 400 related to the forward / reverse of the vehicle, and the shift shaft 200 is provided with a shift clutch 500 constituting the left and right pairs.

The shuttle clutch 400 and the shift clutch 500 operate by hydraulic pressure to have a wet hydraulic multi-plate clutch configuration that selectively allows or blocks the power connection with the driven side.

Internal passages

102 and 202 defining a path through which hydraulic pressure can be provided are elongated along the longitudinal direction of the corresponding axis.

Reference numerals

104 and 204 indicate the hydraulic port to which the hydraulic line is connected to introduce the hydraulic oil into the shuttle shaft 100 and the internal shaft of the transmission shaft 200.

The conventional hydraulic shuttle transmission device has the advantage that the hydraulic assist in the shift to implement the selective power connection, compared to the above-described mechanical type has the advantages of quietness, ease of operation, and the shifting accuracy, but the cooling in the hydraulic clutch applied thereto There is a disadvantage in that the clutch performance is reduced due to leakage of oil.

That is, as shown in a partial enlarged view of FIG. 1, a certain clearance is provided between the oil seal constituting the clutch and the pressure plate to prevent friction loss with the oil seal due to the flow of the pressure plate and to prevent the oil seal from being separated. There is a problem that the oil is drawn out, the cooling performance of the clutch disk and the clutch plate friction heat is lowered, and eventually the hydraulic clutch is squeezed.

An object of the present invention is to provide a wet hydraulic multi-plate clutch capable of minimizing the friction loss between the oil seal and the pressure plate while preventing the leakage of oil introduced into the clutch for cooling.

As a means of solving the problem, the present invention includes a hub gear that is rotatable relative to the clutch housing and the clutch housing, spline coupled to the clutch housing inner diameter surface and the hub gear outer diameter surface so that a plurality of clutch plates and clutch discs are alternately positioned, the clutch A piston is installed in the housing, and a return spring is installed in front of the piston, and the hollow shaft, the piston, the hub gear, and the clutch housing have a passage through which oil flows from the hollow shaft to the outside of the clutch housing, and a snap ring at the clutch housing opening side. The pressure plate is assembled to be constrained through the oil plate, and an oil seal is installed on an outer diameter surface of the hub gear facing the pressure plate inner end, wherein the oil seal outer diameter surface is formed with one or more contact protrusions contacting the inner end of the pressure plate. Provide hydraulic multi-plate clutch.

Here, the contact protrusion may be a semi-circular protrusion that is convexly curved at the center.

Alternatively, the contact protrusion may be a triangular protrusion with a tip formed at the center thereof.

In addition, the contact protrusion may be an inclined protrusion inclined into the clutch having the oil.

As another example, a groove surface in which the contact protrusion is in contact with the inner end of the pressure plate may be further formed, and the contact protrusion may be formed to have a length capable of contacting the groove surface.

At this time, the groove portion is preferably formed in a larger width than the width of the contact projection.

According to the wet hydraulic multi-plate clutch according to the embodiment of the present invention, the pressure plate and the oil seal come into close contact with each other without a gap by a contact protrusion formed in the oil seal and contacting the pressure plate. Therefore, leakage of oil introduced into the clutch for cooling purposes can be prevented, and thus the cooling effect on the frictional heat of the clutch disc and the clutch plate can be increased.

In addition, as described above, by implementing an oil seal that contacts the pressure plate with a minimum area by a contact protrusion while preventing oil leakage, the oil seal and the pressure plate are subjected to friction when the movement of the pressure plate occurs in the horizontal direction by the clutch operation by hydraulic pressure. The resulting loss of operating force can be minimized.

1 is a schematic configuration diagram of a conventional agricultural work vehicle shuttle transmission.

2 is a cross-sectional view of a wet hydraulic multi-plate clutch according to an embodiment of the present invention.

3 is a cut away perspective view of the wet hydraulic multi-plate clutch according to FIG. 2;

4 is an enlarged cross-sectional view of a main portion of the clutch shown in FIG. 2;

5 to 7 are enlarged views of main parts according to various embodiments of the present disclosure.

8 is an operational state diagram of the multi-plate clutch according to the present invention.

Hereinafter, exemplary embodiments of the present invention will be described in detail with reference to the accompanying drawings.

2 is a cross-sectional view of the wet hydraulic multi-plate clutch according to an embodiment of the present invention, Figure 3 is a cutaway perspective view of the wet hydraulic multi-plate clutch according to FIG.

2 to 3, the clutch 1 according to the present invention includes a drive side clutch housing 10 and a driven side hub gear 12 that is free to rotate relative to the clutch housing 10. The clutch housing 10 is spline-assembled so as to be integrally rotatable with the shuttle shaft 2 (drive shaft), and the hub gear 12 is rotatably fitted on the hollow shaft 100 of the clutch housing 10 via a bearing.

On each of the inner diameter surface of the clutch housing 10 and the outer diameter surface of the hub gear 12, a plurality of clutch plates 11 and several clutch disks 13 are splined at regular intervals, and the two are alternately positioned to overlap each other. 11 moves horizontally left and right in the clutch housing 10 while being spaced at regular intervals via a retainer 104 which forms an elastic restoring force.

The clutch plate 11 is pushed toward the clutch disk 13 due to the clutch plate 11 pressure caused by the forward movement of the piston 14, and thus they are in a state in which they can transmit power by making surface contact with each other. The transmitted rotational power may be transmitted to the hub gear 12 through the clutch plate 11 and the disk 13 which are in contact with the clutch housing 10.

The piston 14, which presses the clutch plate 11 for clutch connection, is slidably assembled in the clutch housing 10. In addition, a hydraulic chamber 19 is formed between one surface of the piston 14 opposite the clutch plate 11 and the partition 106 in the center of the clutch housing 10, and the hydraulic chamber 19 has a flow path formed inside the shuttle shaft 2. Pressure oil is introduced via 22.

The hydraulic pressure in the hydraulic chamber 19 causes the piston 14 to move from the non-clutch initial position to the clutch connection position to pressurize the clutch plate 11 to realize a power connection, and return spring 17 in front of the piston 14. Is installed and the piston 14 is returned to the initial position when the hydraulic pressure is released by the restoring force generated by the return spring 17.

A spring supporter 16 is installed in the hollow shaft 100 of the clutch housing 10 at a predetermined distance from the front of the piston 14, and one end of the return spring 17 is supported by the spring supporter 16. do. In addition, the pressure plate 15 is assembled to the clutch housing 10 opening side inner diameter surface through a snap ring R to restrain the clutch plate 11 from the outermost side.

The hollow shaft 100, the piston 14, the hub gear 12, and the clutch housing 10 have oil for absorbing clutch friction heat and smoothing the clutch from the hollow shaft 100 toward the outside of the clutch housing 10. A passage (or hole, P1, P2, P3, P4) is formed to flow, and oil is supplied through the flow path 20 formed by the spline of the shuttle shaft 2.

In order to prevent the lubricating and cooling oil introduced into the clutch through the hollow shaft 100 from moving to the position where the clutch disc 13 and the clutch plate 11 are connected to each other, The oil seal 120 is installed on the outer diameter surface of the hub gear 12 facing the inner end of the pressure plate 15, and the contact protrusion contacting the inner end of the pressure plate 15 with the minimum area at the outer diameter surface of the oil seal 120 ( 122 is formed (see FIG. 4).

The contact protrusion 122 may be formed in one or more numbers, and in order to minimize frictional loss during the operation of the pressure plate through the minimum area contact with the inner end of the pressure plate 15, the center is convexly curved as shown in FIG. It may be in the form of a projection, or may be configured in the form of a triangular projection having a tip portion in the center as shown in FIG.

On the contrary, as shown in FIG. 6, if the contact protrusion 122 has the configuration of the inclined protrusion inclined into the clutch in which the oil is present, the pressure plate 15 may be slightly displaced to the outside of the clutch by the pressure of the oil flowing inside the clutch. It is possible to achieve a structure in close contact with the inner end more tightly, it is possible to seal more securely between the pressure plate 15 and the oil seal 120.

On the other hand, as shown in still another embodiment of Figure 7, the inner surface of the pressure plate 15 to further form a groove surface 152 for the contact protrusion 122 is in contact with the contact projection 122 is the groove surface ( If formed to a length that can contact the 152, because the path that the oil leakage between the pressure plate 15 and the oil seal 120 is expected is a curved shape, this is also effective in preventing oil leakage.

At this time, in forming the groove surface 152, as shown in the drawings, when the pressure plate 15 flows due to the clutch operation, the contact protrusions 122 come into contact with both side surfaces of the groove surface 152 to the pressure plate 15 flow. In order not to be an obstacle, it is preferable to form the groove surface 152 with a sufficient width such that the contact protrusion 122 does not touch both side portions of the groove surface 152 when the pressure plate 15 moves.

7 illustrates the contact protrusion 122 of FIG. 4 as an example of the contact protrusion 122 of the oil seal 120, the contact protrusions 122 having the shapes illustrated in FIGS. 5 and 6 are illustrated. Of course, the configuration of the concave surface 152 may also be applied to the oil seal 12 having a.

In the drawing, reference numeral 18 is a spring guide which is assembled to the spring support 16 and positioned to the center of the return spring 15 to guide the compression / restore of the spring 15 smoothly.

The following is a brief look at the wet hydraulic multi-plate clutch operation of the present invention made of the configuration as described above.

8 is an operation state diagram of the multi-plate clutch according to the present invention, Figure 8 (a) is an operating state diagram showing the state that the clutch connection is implemented according to the hydraulic supply, (b) is the hydraulic pressure is released, the clutch connection is released This is a working state diagram.

When the clutch pedal (not shown) is operated for the power connection, the flow path is opened in conjunction with the clutch pedal operation, and the hydraulic oil is supplied to the hydraulic chamber 19 of the clutch along the shuttle shaft inner flow passage 22. The piston 14 moves forward from the non-clutch initial position to the clutch connection position by the pressure generated by the supplied pressure oil on the action surface of the piston 14.

The return spring 15 is compressed by the forward movement of the piston 14 to the clutch connection position, and the forwardly moved piston 14 presses the clutch plate 11. By pressing the piston 14, the clutch plate 11 is pushed in the direction in which the piston is pressed to come into contact with the clutch disk 13, so that power can be transmitted from the clutch housing 10 toward the hub gear 12.

The frictional heat in the clutch connection process, through the passage 20 of the shuttle shaft 2, the clutch through the passage (P1) (P2) formed with the hollow shaft 100 and the piston 14 in which the return spring 15 is located. The oil is absorbed through the oil introduced therein, and the oil exits out of the clutch via the passage P3 of the clutch hub, the gap between the disc 13 and the plate 11, and the passage P4 formed in the clutch housing.

On the other hand, when the hydraulic pressure is released by the clutch operation for power cut or shifting, the piston 14 is retracted in the direction of releasing the clutch connection and returned to its original position by the restoring force acting on the piston 14 by the return spring 16. , The power transmission state is released by the clutch plate 11 spaced apart from the clutch disk 13 according to the retraction of the piston 14.

According to the embodiment of the present invention, the pressure plate and the oil seal are in close contact with each other without any gap by the contact protrusion formed in the oil seal and contacting the pressure plate. Therefore, leakage of oil introduced into the clutch for cooling purposes can be prevented, and thus the cooling effect on the frictional heat of the clutch disc and the clutch plate can be increased.

In addition, by preventing oil leakage as described above, by contacting the pressure plate with a minimum area by the contact projection and realizing a seal, when the movement of the pressure plate occurs in the horizontal direction by the clutch operation by hydraulic pressure, The loss of operating force can be minimized.

In the detailed description of the present invention, only specific embodiments thereof have been described. It is to be understood, however, that the present invention is not limited to the specific forms referred to in the description, but rather includes all modifications, equivalents, and substitutions within the spirit and scope of the invention as defined by the appended claims. Should be.

The present invention can be applied to a wet multi-plate clutch of a hydraulic transmission in which oil is filled in the clutch and smooth clutch regulation is performed by the filled oil and frictional heat is absorbed.

Claims

A clutch housing and a hub gear rotatable with respect to the clutch housing;

Multiple clutch plates and clutch discs are splined to the clutch housing inner diameter surface and the hub gear outer diameter surface such that a plurality of clutch plates and clutch disks are alternately positioned.

A piston is installed in the clutch housing, a return spring is installed in front of the piston,

The hollow shaft, the piston, the hub gear, and the clutch housing have passages through which oil can flow from the hollow shaft to the outside of the clutch housing.

On the clutch housing opening side, the pressure plate is assembled to be restrained through the snap ring,

Wet hydraulic multi-plate clutch, characterized in that the oil seal is installed on the outer diameter surface of the hub gear facing the inner end of the pressure plate, the oil seal outer diameter surface is formed with at least one contact projection contacting the inner end of the pressure plate.
The method of claim 1,

Wet hydraulic multi-plate clutch, characterized in that the contact projection is a semi-circular projection is convexly curved in the center.
The method of claim 1,

Wet hydraulic multi-plate clutch, characterized in that the contact projection is a triangular projection with a tip formed in the center.
The method of claim 1,

Wet hydraulic multi-plate clutch, characterized in that the inclined protrusion inclined into the clutch with oil.
The method according to any one of claims 1 to 4,

Wet surface is formed in the inner end of the pressure plate is in contact with the contact projection is in contact with the contact projection is wet hydraulic multi-plate clutch characterized in that the length formed to be in contact with the groove surface.
The method of claim 5,

The groove surface is a wet hydraulic multi-plate clutch, characterized in that formed in a larger width than the width of the contact projection.