JPH0617691B2 - Friction type automatic starter - Google Patents

Description

Detailed Description of the Invention [Industrial applications]

The present invention relates to a friction-type automatic starting device that combines a wet friction clutch and a forced oil circulation mechanism.

[Prior art]

The automatic starter using a friction clutch such as centrifugal type, electromagnetic type, and pressing force control type has conventionally adopted a dry single plate type clutch mainly for air cooling or even for a wet type clutch depending on heat generation. Since it was not circulated, overheating is likely to occur when used for a long time in a half-clutch state,
Insufficient durability has been a practical problem.

[Problems to be Solved by the Invention]

Therefore, according to the present invention, oil can be circulated according to the amount of heat generated by the clutch due to slippage and cooled by an oil cooler or the like. Therefore, the heat load becomes large, and overheating occurs even when half-clutch operation is continued for a long time. Can be surely prevented,
It is an object of the present invention to provide a friction type automatic starting device which is excellent in practicality and durability.

[Means for solving problems]

The friction type automatic starting device of the present invention has been made in view of the above circumstances, and includes an input shaft connected to a power source, an output shaft concentrically arranged on the input shaft, and the input shaft. The oil pump includes a wet clutch drivingly connected to the output shaft, a case connected to the input shaft for enclosing the wet clutch, and an oil pump for supplying oil into the case. The wet clutch is drivingly connected in parallel between the shaft and the output shaft.

[Action and effect]

The friction type automatic starting device of the present invention is drivingly connected between an input shaft connected to a power source, an output shaft concentrically arranged on the input shaft, and the input shaft and the output shaft. It comprises a wet clutch, a case connected to the input shaft to enclose the wet clutch, and an oil pump for supplying oil into the case, the oil pump being provided between the input shaft and the output shaft. Since it has a configuration in which it is drivingly connected in parallel with the clutch, the oil pump is driven when the relative rotation of the input shaft and the output shaft occurs, that is, when the wet clutch is slipping, so that the amount of heat generated depends on the amount of heat generation. The oil can be circulated and cooled, so that the heat load becomes large, and even if the half-clutch operation continues for a long time, overheating of the clutch can be reliably prevented, and the practicality and durability are excellent. Further, when the wet clutch is securely engaged, the relative rotation between the input shaft and the output shaft is lost and the oil pump is not driven, so that it is possible to minimize the power loss.

【Example】

Next, the present invention will be described based on an embodiment shown in the drawings. Reference numeral 1 is an input shaft, 2 is an output shaft, 3 is a friction type automatic starting device according to the present invention, and 11 is a drive disk fastened to an end surface of the input shaft 1 at a central portion. The friction automatic starting device 3 includes a friction automatic starting device case 4, a wet multi-plate clutch 5 and an oil pump 8 provided in the case 4. The case 4 includes a disk-shaped front cover 44 whose input shaft side surface is fastened to the drive disk 11 at the outer peripheral portion, a cylindrical case body 47 which is tightened on the output shaft side surface of the front cover 44, and the case body. In the present embodiment, a disk-shaped rear cover 48 fastened together with the case body 47 is formed on the side surface of the output shaft 47. An oil pump mounting seat 41 and a suction oil passage 42 are provided in the center of the inner wall of the front cover 44, and a weight fitting recess for a centrifugal clutch is provided in the outer periphery of the front cover 44.
A weight room 43 which is set to 0 is formed. An inner peripheral spline 45 is formed in the case body 47, and a return spring mounting cylinder chamber 46 of the centrifugal clutch is formed in the wall. The wet multi-plate clutch 5 includes a multi-plate friction surface 51 arranged on the outer peripheral portion of the case body 47, a centrifugal clutch engagement mechanism 6 provided between the multi-plate friction surface 51 and the front cover 44, A clutch wheel 55 connecting the multi-disc friction surface 51 and the output shaft 2, a damper 57 provided in the clutch wheel 55, and a pressing force provided on the left side of the multi-disc friction surface 51 and the clutch wheel 55. It comprises a controllable clutch release mechanism 7. The multi-plate friction surface 51 has a separator plate 511 having an outer circumference spline-fitted to the inner circumference of the case body 47, and an inner circumference spline-fitted to an outer cylindrical surface of the clutch wheel 55,
The friction plates 513 are alternately stacked on the separator plates 511. The clutch wheel 55 includes the friction plate 513.
Has an outer peripheral spline 551 fitted with a spline, a cylinder 552 having a large number of oil circulation holes 56 formed therein, a hub 555 spline fitted with the output shaft 2, and an annular plate-like member integrally formed with the cylinder 552. The drive plate 557 is composed of driven plates 558 and 559 whose inner circumference is connected to the hub 555 so as to sandwich the drive plate 557. The damper 57 is a window 5 provided on the drive plate 557.
71, the driven plates 558 and 55 corresponding to the window 571
It is composed of spring covers 574 and 575 provided on the plate 9 and a spring 577 inserted into a spring room formed by the window 571 and the spring covers 574 and 575. The centrifugal clutch engagement mechanism 6 is inserted into a pressure plate 61 which is placed on the right side of the multi-plate friction surface 51 and also serves as a separator plate, and the pressure plate 61 and a weight room 43 provided on the inner wall of the front cover. It comprises a centrifugal weight 62, a cam surface 430 of the front weight room 43, and a return spring 63 mounted inside the cylinder chamber 46 of the case body wall and installed behind the pressure plate 61. The clutch release mechanism 7 includes an operation lever 71 that is rotationally displaced around a fulcrum 711 provided in a housing 10 that houses the friction automatic starter 3, and a flange that abuts the tip of the lever 71.
A bearing case 72 having 721, a right end portion of which is provided by penetrating into the case 4 through a gap between the inner circumference of the rear cover 48 and the output shaft 2, and is rotatably supported by the output shaft 2 through a slitted metal bearing 73. Sliding sleeve 74, bearing case 72 and sliding sleeve 74
The inner periphery of the bearing 75 and the right end of the sliding sleeve 74 interposed between the inner periphery of the rear cover 48 and the inner periphery of the rear cover 48 are engaged with the rivet 76, and the outer periphery overlaps the left side of the friction surface 51. It is composed of a diaphragm spring 78 that is in contact with a pressure ring 77 that is provided. An oil seal 79 is attached between the outer circumference of the sliding sleeve 74 and the inner circumference of the rear cover 48. The oil pump 8 includes an oil pump cover 81 fastened to the oil pump mounting seat 41 of the front cover 44, and the cover 81.
Internal gear 82, which is fitted in such a way that it can rotate and slide freely, output shaft 2
External gear 83, which is spline-fitted to the tip 21 of the external gear, is provided so as to mesh with the internal gear 82, and an oil pump mounting seat.
The partition plate 84 is sandwiched between the seat surface of 41 and the cover 81. The oil pump 8 pumps oil through the oil passage 22 provided at the shaft center of the output shaft 2, the central hole 841 of the partition plate 84, the suction oil passage 42 of the front cover, and the suction port 842 provided in the partition plate 84. It is sucked and discharged from the discharge port 811 provided in the cover 84 into the case 4. The oil discharged into the case 4 is
The oil passes through the friction surface 51 mainly through the oil circulation hole 56 of the wheel 55 and is supplied to an oil cooler (not shown) through a gap between the sliding sleeve 74 and the input shaft 1, and the oil in the output shaft 2 is supplied from the oil cooler. Circulated to road 22. The oil pump 8, the centrifugal clutch engagement mechanism 6, and the clutch release mechanism 7 operate as follows. [Oil Pump 8] When heat is generated, that is, when the clutch is in a half-clutch state, the front cover 44 which is a driving side member of the clutch and the output shaft 2 which is a driven side member of the clutch.
By utilizing the difference in the number of revolutions between and, the oil pump is driven to cool the clutch. Therefore, when the clutch is engaged (when heat is not generated), the oil pump does not operate and power loss can be minimized. [Centrifugal Clutch Engagement Mechanism 6] When starting, it operates as a normal centrifugal clutch. The clutch pressing force is determined by the balance with the reaction force generated by the diaphragm spring 78 on the opposite side, and the maximum torque capacity is generated when the weight 62 hits the outer inner peripheral wall 431 of the weight room 43, and more torque is generated. It is not the capacity. The centrifugal weight 62 tries to be pushed outward in the radial direction by a force proportional to the square of the engine speed due to the centrifugal force, but this is converted into an axial force by utilizing the wedge effect by the cam surface 430, The pressure plate 61 is pressed to secure the torque capacity corresponding to the input rotation speed. The return spring 63 is installed behind the pressure plate 61, and when idling, pushes back the centrifugal weight to prevent the clutch from dragging. FIG. 2 shows the relationship between the input shaft speed and the clutch pressing force. [Clutch Release Mechanism 7] a) Control the torque capacity of the centrifugal clutch engagement mechanism 6,
Protects transmission system members from shock overload. b) Allow neutral (shut off power) while driving. c) When the input shaft is connected to the vehicle engine, it functions as a parking mechanism that uses the friction torque of the engine. For the above three purposes, the clutch operating lever 71 is controlled by an actuator using engine negative pressure,
Perform the required operation. FIG. 3 shows the relationship between the load on the friction surface by the diaphragm spring 78 and the displacement of the diaphragm spring. Further, the operation according to the usage state when the friction type automatic starting device is mounted on an automobile is as follows. [During parking (when the engine is stopped)] Since the conventional centrifugal clutch could not be engaged during parking, the friction torque of the engine could not be utilized, but this can be achieved using the diaphragm spring 78 in the present invention. . The friction torque of the engine is about 1/3 of the maximum torque, so a small pressing force is sufficient. Therefore, it has the advantage that no special parking mechanism is required. [At the time of neutral] By operating the operation lever 71, the diaphragm spring 78 is deflected to near the point C shown in FIG. 3 to eliminate the axial load of the centrifugal weight 62. (At this time, the weight 62 is in contact with the outer inner peripheral wall 431 of the weight room 43.) [At the time of starting] The diaphragm spring 78 is deflected to a range larger than the point A and smaller than the point B, and the clutch is released from the parking state to serve as a centrifugal clutch. To start. Point B'in the figure is a point showing the lower limit at which the deflection of the diaphragm spring 78 decreases and the pressing force changes when the clutch plate wears. By setting the displacement of the centrifugal weight and the deflection of the spring so as to pass the maximum value near the point B in this way, it is possible to prevent the torque capacity of the clutch from decreasing due to wear of the clutch plate. [Driving] Due to the balance between the centrifugal weight 62 and the reaction force of the diaphragm spring 78, a pressing force is generated so that the vehicle can travel in a directly connected state. Since it is a multi-plate type, this pressing force is small, and the operating lever 71 is easy to operate (for example, the maximum torque is 14 kgm.
In the case of a clutch suitable for the engine of [6 friction plates, radius of about 80 mm], about 75 to 150 kg is enough. ), The drive mechanism can be made compact. Disadvantages of conventional centrifugal clutches are: (a) Since the centrifugal weight does not work during parking, the clutch becomes neutral and parking due to engine friction is not possible, so a separate parking mechanism is required. (B) To make the clutch in neutral while running,
It is necessary to push back the centrifugal weight with great force. However, in the present embodiment, the above-mentioned two points can be easily solved because it depends on the balance of the forces of the centrifugal weight and the diaphragm spring. FIG. 4 shows a second embodiment of the present invention. In this embodiment, the clutch release mechanism 7 in the first embodiment is omitted. FIG. 5 shows a third embodiment of the present invention. In this embodiment, a diaphragm spring 78 and a centrifugal weight 62 are used.
This is achieved by arranging and in series. Differences from the first embodiment are as follows. [During parking] Engine friction torque is used by the pressing force of diaphragm spring 78 to park. [Neutral] Move the clutch operating lever 71 to the left in the figure to release the clutch. [Starting] The clutch operating lever 71 is moved a little from the parking state (on the left side in the above figure), the clutch is released, and the centrifugal weight 62 starts pressing with the increase in the engine speed. [Driving] The centrifugal force 62 and the diaphragm spring 78 are used to establish a direct connection. Since the pressing force may be small because it is used with multiple plates (about 75 to 100 kg), the drive mechanism for driving the clutch operating lever 71 becomes compact. FIG. 6 shows a fourth embodiment. In this embodiment, the centrifugal clutch engagement mechanism 6 in the fourth embodiment is omitted. FIG. 7 shows a fifth embodiment. In this embodiment, a wet multi-plate electromagnetic clutch 7'is used as a clutch engagement and disengagement mechanism. FIG. 8 shows a sixth embodiment. In this embodiment, the engine brake clutch 9 is used. In this embodiment, the power transmission is divided into a flow through the one-way clutch and a flow not through the one-way clutch to avoid sudden engagement at the time of starting which occurs when the load torque of the clutch falls below the clutch torque capacity. That is, when the accelerator pedal is suddenly turned off, such as during start-up acceleration, the load torque of the clutch falls below the torque capacity of the clutch, the clutch that had been slipping up to that point suddenly engages, and shock is generated when the engine is driven backward from the vehicle side. Occurs. To avoid this, create a flow of power through the one-way clutch to avoid reverse drive from the vehicle side. However, since the engine brake does not work because of the one-way clutch, the flow that does not go through the one-way clutch is added to achieve engine braking. FIG. 9 shows another embodiment of the driving method of the oil pump 8 applicable to the first to sixth embodiments. One member of the oil pump 8 (for example, pump casing)
A friction plate (a facing plate) that operates by the pressing force of the centrifugal weight 62 is attached to 81), and the other member of the oil pump 8 (for example, an external gear) is connected to the output shaft 2. Since the drive torque of an oil pump with a discharge pressure of about 3 to 4 kg / cm and a discharge rate of about 14 cc is usually 0.3 kgm, if an oil pump drive friction plate is installed in parallel with the friction plate of the starting wet multi-plate clutch, Due to the relationship of the torque capacities required for synchronizing the respective clutches, under the same pressing force, the oil pump driving friction plate completes the synchronization earlier than the starting friction plate. Therefore, a rotation difference occurs between the members of the oil pump,
As heat generation of the starting clutch begins to occur, the oil pump is driven and the cooling oil circulates. The advantage of this configuration is that when the oil pump driving method of the first to sixth embodiments is in neutral, the oil pump is driven, drag occurs, and complete neutral cannot be obtained. Because only by dragging,
This means less drag when in neutral. This can be further improved by adding a wave amount and a camber amount to the friction plate. 10 to 15 are examples of the oil groove A in the lining of the friction plate 513. By thus forming the oil groove A in the friction plate, oil smoothly flows through the friction surface 51, and the cooling effect of the friction surface can be increased. As described above, the friction-type automatic starting device of the present invention includes an input shaft connected to a power source, an output shaft concentrically arranged on the input shaft, and a drive between the input shaft and the output shaft. It comprises a connected wet clutch, a case connected to the input shaft for enclosing the wet clutch, and an oil pump for supplying oil into the case. The oil pump is provided between the input shaft and the output shaft. Since it has a configuration in which it is drivingly connected in parallel with the wet clutch, the oil pump is driven when relative rotation of the input shaft and the output shaft occurs, that is, when slippage occurs in the wet clutch. Oil can be circulated and cooled according to the amount, which increases the heat load and can reliably prevent overheating of the clutch even when half-clutch operation continues for a long time, which is excellent in practicality and durability. It is. Further, when the wet clutch is securely engaged, the relative rotation between the input shaft and the output shaft is lost and the oil pump is not driven, so that it is possible to minimize the power loss.

[Brief description of drawings]

FIG. 1 is a sectional view of a first embodiment of a friction type automatic starting device of the present invention, FIG. 2 is a graph showing characteristics of centrifugal weight and clutch pressing force, and FIG. 3 is a spring load and displacement amount of a diaphragm spring. FIG. 4 is a skeleton diagram showing a second embodiment of the friction automatic starting device of the present invention, FIG. 5 is a skeleton diagram showing a third embodiment of the friction automatic starting device of the present invention, and FIG. Is a skeleton diagram showing a fourth embodiment of the friction automatic starting device of the present invention, FIG. 7 is a skeleton diagram showing a fifth embodiment of the friction automatic starting device of the present invention, and FIG. 8 is a friction type of the present invention. A skeleton diagram showing a sixth embodiment of the automatic starting device, FIG. 9 is a skeleton diagram showing a seventh embodiment of the friction type automatic starting device of the present invention, and FIGS. 10 to 15 are lining oil groove patterns of friction plates. Is an example of. In the figure 1 ... Input shaft 2 ... Output shaft 3 ... Automatic friction starter 5 ... Wet multi-plate clutch 6 ... Centrifugal clutch engagement mechanism 7 ... Clutch release mechanism 8 ... Oil pump 57 ... Damper 62 …… Centrifugal weight 78 …… Diaphragm spring 81 …… Oil pump cover (one member) 82 …… Internal gear 83 …… External gear (other member)

Claims (2)

[Claims] 1. An input shaft connected to a power source, an output shaft concentrically arranged on the input shaft, a wet clutch drivingly connected between the input shaft and the output shaft, It comprises a case connected to an input shaft for enclosing the wet clutch, and an oil pump for supplying oil into the case. The oil pump is arranged between the input shaft and the output shaft in parallel with the wet clutch. A friction type automatic starting device characterized by being drive-connected. 2. The oil pump has one member connected to the input shaft and the other member connected to the output shaft, and is driven according to relative rotation between the input shaft and the output shaft. The friction type automatic starting device according to claim 1, characterized in that