JPH033824B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a lubricating device for an automobile transmission,
In particular, the present invention relates to a device that performs lubrication using pressure oil for controlling a transmission.

Conventionally, lubrication systems for automobile transmissions have generally been of the so-called raking type, in which lubricating oil is scraped up directly from the oil pool by the transmission gear itself. Kakiage type equipment suffers from stirring power loss due to stirring the oil in the oil reservoir, and it is not possible to supply lubricating oil centrally to the parts where it is needed. Consideration is now being given to adopting a so-called forced lubrication system that can forcibly supply lubricating oil to a small amount and to a specific part. In particular, efforts are being made to put the forced lubrication type lubrication system into practical use, particularly in belt-driven continuously variable transmissions where the lubrication and cooling effects cannot be achieved sufficiently mechanically with the scraping type.

By the way, in order to forcibly supply lubricating oil to the above-mentioned transmission, it is sufficient to install a dedicated hydraulic pump, but not only does it require power to operate, but it also needs to be made compact, lightweight, and In automobiles, where there is a particularly strong demand for cost reduction, it is difficult to employ a dedicated pump, and in this sense, it is desirable to use pressure oil for transmission control. However, when a portion of the pressure oil for transmission control is directly used as lubricating oil, a large amount of the above pressure oil is used for lubrication, and the oil circulation is accelerated, resulting in an agitated lubrication system. The oil is sucked into the control line without air bubbles being sufficiently removed from the hydraulic oil reservoir, and the air bubbles sucked into the control line cause fluctuations in the oil pressure of the control system, making transmission control unstable. Not only that, but in areas where the flow rate of control oil is high, cavitation may occur and damage control valves, pumps, etc.

The present invention was made against this background, and its purpose is to provide an inexpensive lubrication device that uses pressure oil for controlling a transmission, that is, hydraulic oil of a hydraulic drive device. It is an object of the present invention to provide a lubricating device for an automobile transmission that can effectively prevent air bubbles from entering the system's hydraulic oil and can supply lubricating oil intensively to parts of the transmission that require lubrication.

The gist of the present invention is, in order to achieve the above-mentioned object, to use a hydraulic drive device that changes the gear ratio by moving gears, variable speed pulleys, metal V-belts, etc., and the gears. In the automobile transmission, a branch passage branched from the hydraulic oil passage of the hydraulic drive device is connected to an injection nozzle of the ejector, and lubricating oil is removed from the lubricating oil reservoir by injection of hydraulic oil from the nozzle. is pumped up, and the pumped lubricating oil is supplied together with the injected lubricating oil to the lubrication-required parts of the transmission element.

In a lubricating device with such a configuration, a large amount of lubricating oil in the lubricating oil reservoir is supplied to the transmission by a small amount of hydraulic oil injected from the injection nozzle of the ejector, so that the amount of hydraulic oil used for lubrication is reduced. The amount of oil returned from the lubrication system to the control system also decreases. Therefore, the number of air bubbles mixed into the hydraulic oil of the control system is reduced, and the circulation of the hydraulic oil in the hydraulic oil reservoir is slowed down, so that air bubbles are sufficiently removed.
Trouble caused by air bubbles being sucked into the control line will be avoided. Further, since the hydraulic oil is injected from the injection nozzle using the hydraulic oil pressure of the control system, a pump exclusively for lubrication is not required, and the cost of the apparatus can be reduced.

Above, two or three embodiments of the present invention will be described in detail based on the drawings.

FIG. 1 is a diagram showing an embodiment in which the present invention is applied to a belt-driven continuously variable transmission, together with a hydraulic circuit of a hydraulic drive device that supplies hydraulic oil to the transmission, and an electric speed change control circuit. It is.

In the figure, reference numeral 2 denotes a belt-driven continuously variable transmission, such as the one shown in FIG. 2, for example.

In FIG. 2, reference numerals 4 and 6 indicate rotating shafts provided in parallel to each other, 4 is a driving shaft, and 6 is a driven shaft. These driving shafts 4 and driven shafts 6
The fixed pulleys 8 and 10 are fixedly provided on the shafts (the term "rotary shaft" is used to refer to both shafts), respectively. And each fixed pulley 8
and 10, movable pulleys 12 and 14,
They are provided so as to be able to slide in the axial direction along the rotating shafts 4 and 6, respectively. The movable pulleys 12 and 14 are fitted into the circular cross-sections 20 and 22 of the rotating shafts 4 and 6 in circular holes 16 and 18. In addition, the boss portions 24 of the movable pulleys 12 and 14
A plurality of balls 36 are arranged astride axial grooves 28 and 30 formed on the inner peripheral surfaces of the rotary shafts 4 and 26, and axial grooves 32 and 34 formed on the outer peripheral surfaces of the rotating shafts 4 and 6, respectively. The rotating shafts 4 and 6 of the movable pulleys 12 and 14 are
Relative rotation is prevented. The movable pulleys 12 and 14 and the fixed pulleys 8 and 10 have truncated conical surfaces with extremely large apex angles formed on their opposing end surfaces, and V grooves 38 and 40 are formed between these truncated conical surfaces. is formed. Therefore,
The combination of the fixed pulley 8 and movable pulley 12 forming these V grooves will be referred to as a driving variable speed pulley 50, and the combination of the fixed pulley 10 and movable pulley 14 will be referred to as a driven variable speed pulley 52.

The driving speed change pulley 50 and the driven speed change pulley 5
A metal V-belt 54 is wrapped around 2 and 2. This V-belt 54 consists of a hoop 56 made of a plurality of metal sheets stacked one on top of the other, and a large number of metal blocks 58 inserted through the hoop 56.
The rotational torque of the driving speed change pulley 50 is transmitted to the driven speed change pulley 52 by the blocks 58 which are brought into close contact with each other under the tension of the hoop 56.

A housing 60 having a substantially bottomed cylindrical shape is fixed to the drive shaft 4 with screws 61. The housing 60 is open toward the variable speed pulley 50 and is fitted with the outer peripheral surface of the movable pulley 12. The oil tightness between the movable pulley 12 and the housing 60 and between the movable pulley 12 and the drive shaft 4 is
They are held by O-rings 62 and 64, respectively, and oil-tightness between the housing 60 and the drive shaft 4 is maintained by press-fitting the housing 60 to the drive shaft 4. Therefore, the empty space surrounded by the drive shaft 4, the movable pulley 12, and the housing 60 is isolated from the outside and forms a hydraulic chamber 66.

On the other hand, a piston 68 having a substantially cylindrical shape with a bottom is crimped and fixed to the driven shaft 6 with a screw 69, and the outer circumferential surface of the piston 68 is fitted with the inner circumferential surface of the movable pulley 14 having a substantially cylindrical shape. . piston 68
An O-ring 70 maintains an oil-tight seal between the movable pulley 14 and the movable pulley 14, and an O-ring 72 maintains an oil-tight seal between the movable pulley 14 and the driven shaft 6. That is, a hydraulic chamber 74 is formed surrounded by the driven shaft 6, the movable pulley 14, and the piston 68. In addition, in this case, movable pulley 1
The pressure receiving area of the movable pulley 12 on the driving speed change pulley 50 side is approximately 1/2 of the pressure receiving area of the movable pulley 12 on the drive speed change pulley 50 side. In addition, the hydraulic oil is supplied to the hydraulic chamber 74 through an oil passage 7 formed in the driven shaft 6.
6 directly or from the movable pulley 1
This is done indirectly through an oil passage 78 formed in the boss portion 26 of No. 4. Hydraulic oil is supplied to the hydraulic chamber 66 on the drive speed change pulley 50 side in the same manner.

As shown in FIG. 1, a lubricating oil reservoir 80 is provided below the transmission 2 having such a configuration.
It is adapted to receive lubricating oil falling from the transmission 2. This lubricating oil reservoir 80 is communicated with a hydraulic oil reservoir 84 through a passage 83. The hydraulic oil (same as lubricating oil) in the hydraulic oil reservoir 84 passes through a strainer 86 and is pumped up by a pump 88, passes through a filter 90 and a check valve 92, and then passes through a filter 90 and a check valve 92 to drive the driven shift pulley 52 of the transmission 2. is supplied to chamber 74. Note that the hydraulic pressure in this hydraulic chamber 74 is controlled by an electromagnetic relief valve 94. The hydraulic oil pressure-fed from the pump 88 is also supplied to the hydraulic chamber 66 of the drive speed change pulley 50 while its flow rate is controlled by a three-way electromagnetic flow control valve 96.

On the other hand, the driving pulley 50 and the driven pulley 5
The rotational speeds of the rotating shafts 4 and 6 to which the rotating shafts 2 are attached are detected by sensors 98 and 100, respectively, and the detection signals are input to the main controller 102. The main controller 102 determines the gear ratio of the transmission 2 based on the detection results of both the sensors 98 and 100.
That is, the value obtained by dividing the rotational speed of the driven shaft 6 by the rotational speed of the drive shaft 4 is calculated, and the result is compared with the optimum gear ratio predetermined for each driving state of the automobile, which changes from moment to moment. If the measured gear ratio deviates from the optimum gear ratio, power is supplied to the solenoids of the flow control valve 96 and the relief valve 94 to operate them, and the gear ratio of the transmission 2 is adjusted to match the optimum gear ratio. Controls the amount of oil in the hydraulic chamber 66. In addition, the tension of the V-belt 54 is determined by the driven speed change pulley 52.
The pressure in the side hydraulic chamber 74 is controlled by a relief valve 94 that receives a set pressure command from the main controller 102, and the tension of the V-belt 54 changes momentarily. It is designed to be optimal for the transmission gear ratio. 104,10
5 is a check valve, and the check valve 104 has a high opening pressure.

A pipe line 108 branched from between the relief valve 94 and the check valve 104 is connected to a nozzle 112 in an injection nozzle mechanism 110, which is a type of ejector, installed upright in the lubricating oil reservoir 80. As a result, a portion of the high-pressure hydraulic oil supplied to the hydraulic chamber 74 is guided to the nozzle 112. This injection nozzle mechanism 110 is
It consists of the nozzle 112 and a cylindrical outer cylinder 116 having a small diameter part 114 whose diameter gradually decreases in the middle part. Nozzle 11
2 is the large diameter portion 11 below the small diameter portion 114 of the outer cylinder 116
8, and its injection port is provided to open upward at the small diameter portion 114. On the other hand, the outer cylinder 116 has a lubricating oil suction port 120 at its lower end provided below the lubricating oil surface of the lubricating oil reservoir 80, and a lubricating oil outlet 122 at its upper end.
For example, as shown by the imaginary line in FIG. 2, the V-belt 54 of the transmission 2 is opened toward the inner surface of the intermediate portion on the rising side.

In such an injection nozzle mechanism 110, when hydraulic oil is injected from the injection port of the nozzle 112 at high speed, the air in the small diameter portion 114 around the injection port is removed by the hydraulic oil, and the inside of the large diameter portion 118 is Due to the negative pressure, the lubricating oil in the lubricating oil reservoir 80 is pushed up to the small diameter portion 114 by atmospheric pressure, and the lubricating oil is eventually taken away by the hydraulic oil, and is discharged from the air outlet 122 to the transmission 2. V-belt 54
sprayed towards. Then, as the V-belt 54 rotates, the sprayed lubricating oil including the hydraulic oil is carried toward the upper driving speed change pulley 50 and is scattered around, thereby lubricating the entire transmission 2. becomes.

In this way, in this embodiment, the lubricating oil in the lubricating oil reservoir 80 is mainly used as the lubricating oil for the transmission 2, and the hydraulic oil in the hydraulic drive device, the pressure oil in the so-called control line, is only used in a very small amount. Since it is not used, the amount of hydraulic oil returned from the lubrication system to the control system is significantly smaller than in a lubricating system using hydraulic oil, where all lubrication is taken out from the control line, and the hydraulic oil reservoir 84 is not used.
Air bubbles entering the hydraulic oil reservoir 8 are reduced.
The circulation speed of the hydraulic oil in the control line 4 is reduced to ensure that air bubbles are removed more reliably, thereby preventing the occurrence of adverse effects caused by air bubbles in the control line. Furthermore, since the pressure within the control line is used to inject the hydraulic oil from the nozzle 112 of the injection nozzle mechanism 110, a dedicated pump for lubrication is not required, and the cost of the device is reduced. Furthermore, in this embodiment, a lubricating oil reservoir 80 that receives lubricating oil falling from the transmission 2 and a hydraulic oil reservoir 84 that supplies hydraulic oil to the hydraulic drive device are separated and connected by a passage 83. As a result, air bubbles entering the control system from the lubrication system can be more effectively reduced. However, the lubricating oil reservoir 80 and the hydraulic oil reservoir 84
It goes without saying that the present invention can be carried out even if the lubricating oil reservoir is constructed by integrating the lubricating oil reservoir.

Further, in the embodiment, the lubricating oil outlet 122 is located at the V
Since it is provided toward the inner surface of the belt 54,
Its lubrication and cooling effects are effectively performed. However, in addition to spraying the lubricating oil directly onto the inner surface of the V-belt 54, it is also possible to spray the lubricating oil from the side of the V-belt 54 into the space surrounded by the V-belt 54. be. Furthermore, even if the outlet 122 is not directly provided at the extended end of the outer cylinder 116 of the injection nozzle mechanism 110, the lubricating oil can be supplied using another pipe or a diversion plate that simply changes the direction of the lubricating oil. It may also be guided to a desired location.

Furthermore, in the above explanation, it has been assumed that the rotation axes 4 and 6 are provided above and below, but it is assumed that they are arranged horizontally or at a predetermined inclination with respect to the horizontal. It goes without saying that the present invention can also be applied to. In this case, since the distance from the ejector to the lubricating oil outlet can be made shorter, lubricating oil can be more effectively supplied with the same pressure of hydraulic oil.

Further, in the above embodiment, the pipe line 108 that guides the hydraulic oil to the injection nozzle mechanism 110 is branched from the downstream side of the relief valve 94 that regulates the high pressure in the control line, so as to maintain the control line at a predetermined pressure. Since the residual pressure of the consumed hydraulic oil is used to inject the hydraulic oil from the injection nozzle 112, there is an advantage that the power consumption of the pump 88 does not increase due to the injection of the hydraulic oil. However, if it is necessary to increase the injection pressure of the hydraulic oil, it is also possible to branch the pipe line 108 from upstream of the relief valve 94.

Furthermore, the present invention can be applied to transmissions other than the belt-driven continuously variable transmission as described above.
An example of this will be explained based on FIG. Components having the same functions as those in the embodiment described above are designated by the same reference numerals, and detailed description thereof will be omitted.

In FIG. 3, reference numeral 124 is a gear transmission, and is configured such that a master gear 128 provided on a main shaft 126 and a sliding gear 132 provided on a counter shaft 130 are meshed with each other. The injection nozzle arrangement 1 is placed above the gears 128 and 132 of the transmission 124.
The outlet ports 122 of the ten outer cylinders 116 are opened to supply lubricating oil to the gears 128 and 132. In the figure, reference numeral 134 is a hydraulic control mechanism that moves a predetermined sliding gear along a spline provided on the subshaft in response to commands from the electrical main control device 136.
Through this control, a predetermined gear ratio can be obtained. A pipe line 142 branched from the downstream side of the relief valve 140 that regulates the hydraulic pressure supplied to the hydraulic control mechanism 134 is connected to the nozzle 112 of the injection nozzle mechanism 110, so that hydraulic oil is injected. ing.

As explained above, the present invention can be widely applied to automobile transmissions in which the gear ratio is changed by moving predetermined elements constituting the transmission using hydraulic pressure, and other suitable It goes without saying that the present invention can be implemented with various modifications and improvements based on the knowledge of those skilled in the art without departing from the spirit of the present invention.

[Brief explanation of the drawing]

FIG. 1 is a simplified diagram showing an embodiment of the present invention applied to a lubricating device for a belt-driven continuously variable transmission, and FIG. 2 shows the belt-driven continuously variable transmission and the lubricating oil outlet. It is a front sectional view showing an example of an opening position. FIG. 3 is a simplified diagram showing an embodiment in which the present invention is applied to a lubrication device for a gear transmission. 2: Belt-driven continuously variable transmission, 4: Drive shaft (rotating shaft), 6: Driven shaft (rotating shaft), 8, 10: Fixed pulley, 12, 14: Movable pulley, 38, 40:
V groove, 50: Drive speed change pulley, 52: Driven speed change pulley, 54: V belt, 60: Housing, 6
8: Piston, 66, 74: Hydraulic chamber, 80: Lubricating oil reservoir, 84: Operating oil reservoir, 94: Electromagnetic relief valve,
96: Three-way electromagnetic flow control valve, 98, 100: Sensor, 104: Check valve, 102, 136: Main controller, 108, 142: Pipe line, 110: Injection nozzle mechanism, 112: Nozzle, 114: Small diameter section , 11
6: Outer cylinder, 122: Lubricating oil outlet, 124: Gear transmission, 128: Original gear, 132: Sliding gear, 1
34: Hydraulic control mechanism, 140: Relief valve.

Claims (1)

[Scope of Claims] 1. An automobile transmission comprising a transmission element such as a gear, a variable speed pulley, or a metal V-belt, and a hydraulic drive device that changes the gear ratio by moving the element, A branch passage branched from the hydraulic oil passage of the hydraulic drive device is connected to an injection nozzle of an ejector, and lubricating oil is pumped up from a lubricating oil reservoir by injection of hydraulic oil from the nozzle, and the pumped lubricating oil is A lubrication device for an automobile transmission, characterized in that the injected lubricating oil is supplied to a location requiring lubrication of the transmission element.