JPS6338747A - Centrifugal hydraulic pressure correcting device for belt type continuously variable transmission - Google Patents

Abstract

PURPOSE:To properly correct the centrifugal hydraulic pressure in a high revolution region by arranging a nozzle at the opposed position to a lead port outside a balance chamber and jetting the low hydraulic pressure introduced into the nozzle, into the balance chamber. CONSTITUTION:A line pressure is always supplied into the hydraulic chamber 55 of a secondary pulley 37, and a pulley pushing force acts, and the lubricating oil pressure having the reverse characteristic to the line pressure is introduced into a nozzle 60 and jetted out from injection ports 62 and 63. The nozzle 60 is formed nearly horizontally, in close contact with a gear boss part 43a, at the opposed position to a leak part 56a opened onto the hydraulic balance chamber 56 of the secondary pulley 37, and the injection port 62 is faced to the lead port 56a. When the speed change ratio shifts to a high speed stage, the leak port 56a is brought close to the injection port 62 by the retreat of the pulley 37b and a cylinder 51. Further, a necessary quantity of lubricating oil is certainly supplied into the balance chamber 56 from the injection port 62 through the leak port 56a by the increase of the lubricating oil due to the reduction of the line pressure, and each centrifugal hydraulic pressure in the oil chamber 56 and the balance chamber 56 can be offset.

Description

[Detailed description of the invention]

[Industrial Application Field 1] The present invention relates to a centrifugal hydraulic pressure correction device for correcting centrifugal hydraulic pressure generated in a cylinder of a secondary pulley in a high rotation range in a belt-type thermal stage transmission for a vehicle. This type of belt-type continuously variable "a" machine has a drive belt wrapped around the engine-side priming boot and the wheel-side secondary boot.

), each pulley's movable bobbin is equipped with a hydraulic servo mechanism. Then, the pulley interval is adjusted by moving the movable bobbin in the axial direction using hydraulic pressure, and the diameter ratio of the winding of the secondary pulley around the primary pulley of the belt is changed to achieve continuously variable speed. Therefore, the secondary pulley speeds up as the gear shift progresses to the higher speed side, and during overdrive, the speed increases by a maximum of 2 to 3 times the primary rotation speed. Therefore, the hydraulic pressure inside the cylinder of the secondary pulley is similarly rotated at high speed, and this centrifugal hydraulic pressure is generated, which acts on the secondary pulley separately from the secondary hydraulic pressure. In this way, this centrifugal oil pressure acts to return the gear to the low gear side when shifting to the high gear side, causing an excessive boob pressing force during overdrive. A countermeasure for hydraulic problems and a lever compensation system (4) has been proposed. This is done by installing a hydraulic chamber on one side of the plunger and a balance chamber on the opposite side inside the cylinder of the secondary lever. Then, by inserting an orifice into the plunger, a part of the secondary hydraulic pressure in the hydraulic chamber can be leaked and supplied to the balance chamber, or as shown in Japanese Patent No. 60-104848, an oil guiding plate or an oil passage can be used to balance the hydraulic pressure. Refuel each room separately.In this way,
The centrifugal hydraulic pressure generated in the hydraulic chamber in the high rotation range is offset by the centrifugal hydraulic pressure in the balance chamber. [Problem to be Solved by the Invention 1] By the way, regarding the method of supplying oil to the balance chamber, oil leakage occurs even when the oil pump is at its lowest efficiency in the idle link or low rotation range, unlike the prior art method using an orifice. According to the latter of the prior art, the pump capacity has to be increased by that amount.Also, according to the latter of the prior art, the number 11 is multi-connected, and special holes are machined in the axial and radial directions of the shaft, which improves workability and strength. Undesirable. Furthermore, the method of using the line pressure of the hydraulic chamber as the oil supply source to the balance chamber, as in the former prior art, simplifies the structure, but leaks the line pressure, which directly affects the boob pressing force. Undesirable. The present invention has been made in view of these points, and provides a belt-type continuously variable transmission that uses an oil supply source different from line pressure and has a simple configuration to accurately correct centrifugal oil pressure in a high rotation range. The purpose of the present invention is to provide a centrifugal hydraulic correction device. Means for Solving Problem C 1 In order to achieve the above object, the present invention generates low hydraulic pressure in addition to line pressure in the hydraulic control system of a belt type continuously variable transmission, and in particular, the iT ','The focus is on the fact that the crushing oil pressure increases as the input rotational speed increases at high speed stages with a small gear ratio, making it suitable as a source of oil supply to the balance chamber. Therefore, we installed two hydraulic chambers inside the cylinder of the secondary pulley on one side and a balance chamber for centrifugal hydraulic pressure correction on the other side.
The balance chamber has a configuration in which a leak port is always opened closest to the center, and a nozzle is disposed outside the balance chamber at a location facing the leak port, and low oil pressure from a hydraulic control system is guided to the nozzle. It is constructed so that oil can be sprayed from the leak into the balance chamber. [Function] Based on the above configuration, when shifting to a high speed gear with a small gear ratio, the leakage port of the balance chamber approaches the nozzle as the gap between the crank pulleys becomes wider, and the increased low oil pressure oil flows from the nozzle. A large amount of oil is injected into the balance chamber to generate centrifugal oil pressure, which offsets and corrects the pressure in the oil pressure chamber. Therefore, in the present invention, it is possible to easily and accurately supply oil to the balance chamber with a nozzle using the existing leakage hole in the balance chamber without affecting the boob pressing force with a slip pressure of 1'+1. becomes.

【Example】

Hereinafter, one embodiment of the present invention will be specifically described with reference to the drawings. In FIG. 1, an example of a belt-type continuously variable transmission to which the present invention is applied will be described. Reference numeral 1 is an electromechanical powder clutch, 2 is a continuously variable transmission, and the continuously variable transmission 2 can be broadly classified into two types: , 19 for forward and backward movement from the input side! Part 3. The pulley ratio conversion section 4 J3 and the final reduction section 5 are configured in a transmission line. A lightning powder type lug 1 is housed in one side of the clutch housing 6, and the main case 7 is connected to the other side of the clutch housing G, and the main case 7 is connected to the opposite side of the clutch housing 6. Inside the side case 8, there is a switching section 3 for the continuously variable transmission 1 and 2. A boolean ratio conversion section 4 and a final reduction section 5 are assembled. 7Eila powder type clutch 1 includes a ring-shaped drive member 12. which is integrally connected to a crankshaft 10 from an engine via a drive plate 11. A disk-shaped driven member 14 is spline-coupled integrally with the transmission input shaft 13 in the rotational direction. And driven member 1
A coil 15 is built in on the outer peripheral side of both members 12.4.
A gap 16 is formed along the circumference between 14, and this gap 16 communicates with a powder chamber 17 containing electromagnetic powder inside the gap 16. In addition, a power supply brush 19 is connected to the slip ring 18 of the hub portion of the driven member 14 equipped with the coil 15, and is further connected to the coil 15 through the inside of the driven member 14 from the slip ring 18 to form a clutch current circuit. has been done. In this way, when a clutch current is applied to the coil 15, the drive and driven member 12.1 are connected through the gap 1G.
Due to the magnetic lines of force generated between the clutches 4 and 4, electromagnetic particles are combined and accumulated in the gap 16 in a chain-like manner, and the resulting binding force causes the driven member 14 to slide and be integrally connected to the drive member 12, resulting in a clutch disengaged state. . On the other hand, when the clutch current is cut, the drive due to the electromagnetic powder and the coupling force between the driven members 12 and 14 disappear and the clutch becomes disconnected. In this case, the clutch current is controlled by continuously variable speed l5.
If the operation of the switching unit 3 of 12 is performed by moving, P
Clutch 1 is automatically disengaged when switching from the (parking) or neutral (N) range to the D (drive) or Ds (swift drive) or reverse R (reverse) range. Cludge beggle operation becomes unnecessary. Next, in the continuously variable transmission 2, the switching section 3 connects the input shaft 13 from the clutch 1 and the main shaft 2 disposed coaxially therewith.
0. That is, the input shaft 13 is formed with a reverse drive gear (721) which also serves as the forward engaged side, and the main shaft 20 is rotatably fitted with one gear 22 on the reverse engaged side. Gears 21 and 22 are meshed with each other via a counter gear 24 supported by @23 and an idler gear 2G supported by a shaft 25 (1). A switching mechanism 27 is provided between the main shaft 20 and the gears 21 and 22. Here, the gears 21, 24, 26, 22, which are always in mesh, are connected to the driven member 14 having the coil 15 of the clutch 1, and the inertia mass of this part is relatively large when the clutch is disengaged. Correspondingly, the switching mechanism 27 has splines on the hub 28 of the main @20.
A mating sleeve 29 is configured to be matingly coupled to each gear 21, 22 via a synchronizing mechanism 30, 31. As a result, in the neutral position of the P or N range, the sleeve 29 of the switching mechanism 27 only engages with the hub 28, and the main @2
0 is disconnected from input @13. Next, the sleeve 29
When meshed with the gear 21 side via the synchronization mechanism 30,
The main @20 is directly connected to the input shaft 13, resulting in the forward state of the D or OS range. On the other hand, the sleeve 29 is reversely meshed with the gear 22 side via the synchronizing mechanism 31 1! Then, the input shaft 13 is connected to the main shaft 20 through the gears 21, 24, 26, 22, and the engine power is decelerated and reversed to enter the R range reverse travel state. In the pulley ratio conversion unit 4, a sub-shaft 35 is arranged parallel to the main shaft 20, a primary pulley 3G and a secondary pulley 37 are provided on both of these shafts 20.35, and an endless belt is provided between both pulleys 36.37. drive belt 3
The fourth stage is a handover. The pulleys 36 and 37 are each divided into two parts, one of which is a fixed pulley 36a. 37a, the other movable pulleys 36b, 37b are movable to make the pulley interval variable, and the movable pulley 36
1), 371) are equipped with hydraulic servo devices 38 and 39 that also serve as pistons, and are further equipped with secondary pulleys 3
A spring 40 is applied to the movable pulley 37b of No. 7 in a direction that narrows the interval between the pulleys. Further, as a hydraulic control system, an oil pump 41 manufactured by ea is installed next to the primary pulley 36. This oil pump 41 is a high-pressure gear pump, and the pump drive shaft 42 is connected to the primary pulley 36. Main shaft 20 and input shaft 1
3 and is directly connected to the crankshaft 10 to generate oil pressure during engine operation. And control the oil pressure of this oil pump 41! 20, oil is supplied and drained to each hydraulic servo device 38 and 39, and the pulley spacing between the primary pulley 36 and the secondary pulley 37 is changed to an inverse relationship, thereby making the pulley ratio of the pulleys 3G and 37 of the drive belt 34 stepless. The converted and continuously variable power is output to the subshaft 35. In the final reduction section 5, the minimum pulley ratio on the high speed stage side of the boolean conversion section 4 is very small, for example, 0.5, and therefore
In view of the fact that the number of revolutions of the output shaft 5 is high, the output shaft 44 is connected to the subshaft 35 via a set of intermediate reduction gears 43. A final gear 46 meshes with the drive gear 45 of this output shaft 44, and the final gear 4G is connected to the differential mechanism 4.
Power is transmitted to the axles i and 49 of the left and right drive wheels via the axle 7. 2), the hydraulic servo device 39 of the secondary pulley 37 will be described in detail.
A ball spline 50 is fitted to the single shaft 35 so as to be movable in the axial direction, and one end of a stepped cylinder 51 is attached to the movable pulley 37b. Further, one end of a stepped cylindrical plunger 52 is integrally fixed to the subshaft 35 by a fitting 53, and the other end of this plunger 52 is sealed inside the cylinder 51 with an O-ring 54 to make it liquid-tight. They are mated. Inside the cylinder 51, a hydraulic chamber 55 is formed on the boob side of the plunger 52, and a balance chamber 56 is formed on the opposite side.
Line pressure is supplied through a passage 57 of the movable pulley 37b. The plunger 52 and the cylinder 51 are bent in a stepwise manner, and as the cylinder 51 moves backward together with the movable pulley 37b from the low speed gear shown in FIG. 2(2) to shift up.
This increases the volume of the portion of the balance chamber 5G away from the center, and the leak hole 5 is located closest to the center of the balance chamber 5G.
6a is open. Therefore, a nozzle 60 is installed outside the balance chamber 56 at the boss portion 43a of the gear 43 facing the leak port 56a. The nozzle 60 has one end supported on the case 7 side as shown in ) in FIG.
The nozzle 60 has a passage 61 in the axial direction of the nozzle 60, and an ejection port 62, 63 in the direction of the leak port 56a at the tip and the boss portion 43a of the gear 43. The nozzle 60 is preferably made of copper-based alloy or resin (nylon, etc.) with good activity.
Oil discharged from 1 enters the pressure regulating valve 65 and generates a line pressure in the oil passage 66 that varies depending on the gear ratio, etc., and supplies this to the secondary pulley 37 or the gear ratio low control valve 67 to control the primary pulley 36. supply to. Further, a relief valve 69 is provided in an oil passage 68 draining from the pressure regulating valve G5 to generate lubricating oil pressure, which is guided to the nozzle 60 through an oil passage 70. . Here, the lubricating oil pressure has a completely opposite relationship to the line pressure, and as shown in FIG. 3, the lubricating oil pressure has a large value at the high speed stage where the input rotation speed is large and the gear ratio is small. Next, the operation of the centrifugal hydraulic pressure correction device configured as described above will be explained. First, line pressure is always supplied to the hydraulic chamber 55 of the secondary pulley 37 to push the pulley, and lubricating oil pressure with characteristics opposite to the line pressure is guided to the nozzle 60 and ejected from the spout 62.63. It's gushing out. Therefore, in the idle link or low rotation range, the cylinder 51 moves forward together with the movable pulley 3711 by the secondary pulley 37, and the belt wraps around it.

[) Due to the large diameter, it is a low speed gear. At this time, the leakage port 5 of the balance chamber 56
6a 4;t Since it is far from the nozzle 60, the lubricating oil pressure is minimum and there is little oil, the balance chamber 5G is hardly supplied with oil. On the other hand, when the gear ratio shifts to a high speed gear, the movable pulley 37
1) As the cylinder 51 retreats, the leak port 56a of the balance chamber 56 approaches the nozzle 60. Further, as the lubricating oil pressure increases as the line pressure decreases, this oil can be reliably jetted into the balance chamber 56 from the leak port 56a by the jet port 62 as required. When a centrifugal hydraulic pressure is generated in the hydraulic chamber 55 due to an increase in the secondary rotation speed, a similar hydraulic pressure is generated in the balance chamber 56 to offset the centrifugal hydraulic pressure. The oil in the nozzle 60 is always supplied to the boss portion 43a of the gear 43 by the 0 output blower 63, and the contact portions between the two are forcibly lubricated. As shown in , a part of the boss portion 43a of the hook 43 may be press-fitted into the hole 71 of the case 7 to be attached to the vertical CF. It is also possible to use a low oil pressure, for example, a reducing pressure.Furthermore, a relief valve 71 and an orifice l-chair 72 that suppress operation at low pressure can be provided, and in this case, lubrication at low speeds will not be required. Although the embodiment has been described, it is not limited to this. [Effects of the Invention] As described above, according to the present invention, since the nozzle is simply added outside the balance chamber, the structure is simple. ): Easy to install and advantageous in terms of space. Since low oil pressure is used as the oil supply source, there is no effect on the boob pressing force, and sufficient oil is supplied to the balance chamber in the high rotation range of the high speed stage. The centrifugal oil pressure can be corrected with 38 degrees of accuracy. Since the lubricating oil pressure is constantly supplied, there is no delay in oil supply. Since the nozzle is installed in contact with the shaft side, the oil supply is stable and the installation position can be adjusted. There is little variation in the amount of oil supplied due to errors.

[Brief explanation of drawings]

FIG. 1 is a longitudinal rFI view showing an example of a belt type continuously variable transmission to which the present invention is applied, FIG. 2(C) is another circuit diagram, FIG. 3 is a characteristic diagram of water pressure, and FIG. 4 is a sectional view showing another embodiment of the present invention. . 2...Continuously variable transmission, 4...Boot ratio conversion section, 37.
...Secondary pulley, 39...Hydraulic servo'! 1N
IF! , 51... Schilling, 52... Plunger,
55... Hydraulic chamber, 5G... Balance chamber, 56a...
・Leak port, 60... Nozzle, 62.63... Spout, 70... Oil path. Patent applicant Fuji Heavy Industries Co., Ltd. Agent Patent attorney Jundo Kobashi Patent attorney Susumu Tsukii
Figure 2 of basket 2 (C)

Claims (2)

[Claims] (1) In a configuration in which a hydraulic chamber is provided on one side of the cylinder of the secondary pulley and a balance chamber for centrifugal hydraulic pressure correction is provided on the other side, and the balance chamber has a leak port that is always open closest to the center, A centrifugal hydraulic pressure correction device for a belt-type continuously variable transmission, in which a nozzle is disposed at a location facing the leak, and the low hydraulic pressure of the hydraulic control system is guided to the nozzle, and the oil is jetted into the balance chamber from the leak. (2) One end of the nozzle is supported on the case side, the other end is fixed in contact with the shaft side of the secondary pulley, and the sliding contact area between the nozzle and the shaft is lubricated with low oil pressure guided by the nozzle. A centrifugal hydraulic pressure correction device for a belt type continuously variable transmission according to claim 1.