JPS60159468A - Lubricating device in stepless speed change gear - Google Patents

Abstract

PURPOSE:To effectively lubricate a pair of pulleys and a belt wound therearound, by providing an oil feed nozzle in a space defined among the pulleys and the belt. CONSTITUTION:In a space defined among a main pulley 36, a counter pulley 37 and a belt 34 there is disposed and fixed an oil supply nozzle 50 having legs 53 abutting against a partition wall 7c which is formed surrounding around a hole 7b in a wall section partitioning between a pulley converting section and a gear section, so that the nozzle 50 is set in position. An oil pipe 56 is press-fitted into and connected with the oil feed nozzle 50. Further, the nozzle 50 is so arranged that the jet port of the nozzle 50 is directed along the tangential line of a substantially minimum diameter section of the counter pulley 37 on the rotationally advancing side of the belt 34 inside of the belt 34, thereby a part which offers the maximum heat generation may be effectively lubricated.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a lubricating device for a continuously variable transmission for a vehicle, and more particularly to lubricating the belt and pulley portions.

Belt-type continuously variable transmissions have a structure in which pulleys with variable pulley spacing strongly pinch both sides of the metal belt and rotate to output power at a continuously variable speed. A large frictional torque is always generated in the bell 1-, and therefore, lubrication of the pulley and belt parts is essential to ensure smooth movement of the bell 1- and to further cool the bell. Therefore, it has been proposed in the past, for example, in Japanese Unexamined Patent Publication No. 52-98861, to lubricate the portion to the bell 1 by injecting A-il, but in this case, when lubricating from the outside of the belt, only the belt surface is f, 1 slip. As a solution to this problem, a lubrication circuit is installed on the shaft of the C pulley, and the belt is rotated at high speed. It is conceivable to supply lubrication from the pulley shaft, but the pump drive shaft, etc. may pass through the inside of the pulley shaft, making it difficult to form a lubrication circuit.Additionally, an external lubrication circuit is required, resulting in a complicated structure. Become something.

In view of these circumstances, the present invention has been devised to effectively lubricate the bell 1 from the inside, to effectively lubricate the part that generates the most heat, and to mount the lubrication nozzle in such a way that positioning, etc., can be done simply and reliably. The purpose of the present invention is to provide a lubricating device for continuously variable transmissions.

For this purpose, the configuration of the present invention focuses on the fact that there is only a 4-character gap between the pair of pulleys (pulled bell l-), and utilizes the case wall etc. in this space. 4(I
Insert the oil supply nozzle and install it while doing ff & ik.
The bending motion of the belt is at most 0, and the gist is that the part that generates the most heat is directly and efficiently lubricated.

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 electromagnetic) type clutch, 2 is a continuously variable transmission, and 1llll(
(speed change) *Tsuki 2 iJ For different people, the forward/reverse switching section from the input side (the boolean ratio converting section 4 and the final reduction section F) is configured to be transmission-driven. The electromagnetic powder clutch 1 is housed in one side of the clutch housing 6, and the other side of the clutch housing 6 has a main nose 7 connected thereto, and a side of the main case 7 opposite to the clutch housing 6. The switching section 3, ratio converting section 4, and final reduction section 5 of the continuously variable transmission 2 are assembled inside the lead case 8 that is joined to the
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The electromagnetic V) type clutch 1 is connected to the crankshaft 1 from the engine.
The drive member 171 has a ring-shaped drive member 12 that is connected to the drive play 1 via 11 to the drive plate 1, and an ice-shaped driven member 171 that is integrally spline-connected to the transmission input shaft 13 in the rotational direction. , the coil 15 is built into the outer peripheral side of the 1ζ ribbed member 14, and both members 12
．． A V-tube 16 is formed on the circumference between 14 and 14, and this gap 1G is a powder chamber 17 containing electromagnetic powder inside the gap 1G.
I am in communication with. A power supply brush 19 is in sliding contact with the slip ring 18 of the hub portion of the driven member 14 equipped with the coil 15, and is connected from the slip ring 1B through the inside of the triangular member 14 to the coil 15 to form a clutch current circuit. has been done.

In this way, the clutch current flows through the coil 15 and the gear A
・Drive and driven member 12 via the knob 1G,
Due to the lines of magnetic force generated between 14 and 14, electromagnetic particles are combined and accumulated in a chain shape on the tooth 16, and the driven member 14 slides and is integrally connected to the drive member 12 due to the bonding force of J. The clutch becomes connected. On the other hand, when the clutch current is cut, the electromagnetic powder becomes J, the coupling force between the S live and A driven members 12 and 14 disappears, and the clutch becomes disconnected. If this is done in conjunction with the operation of the switching unit 3 of the transmission 2, it will change from the ρ (Purr... Alternatively, when switching to the R (reverse) range for reverse, clutch 1 automatically engages, making it unnecessary to operate the clutch pedal.

Next, in the continuously variable transmission 2, the switching unit 3 is disposed coaxially with the input shaft 13 from the clutch 1.
It is installed between 0 and 0. That is, the input shaft 13 is formed with a reverse drive gear A'21 that also serves as a forward engaged side.
gJE shaft 20 is rotatably fitted with gear 22 on the reverse engaged side, and these gears 21 and 22 are connected via counter gear 24 supported by shaft 23 and idler gear 2G supported by shaft 25. It is constructed by interlocking.

A switching mechanism 27 is provided between the main shaft 20 and the gears 21 and 22. Here, the above-mentioned 5-gear 721.24.26.22 which is always engaged is the coil 1 of the clutch 1.
5, and corresponding to the fact that the inertia mass of this part is relatively large when the clutch is disengaged, the switching mechanism 21 has a sleeve 29 that is spline-fitted to the hub 28 of the main shaft 20. It is configured to be matingly coupled to each gear 21.22 via a mechanism 30.31.

As a result, in the neutral position of P or N range, the switching mechanism 2
The sleeve 29 of No. 7 is fitted only with the hub 28, and the main shaft 20
is separated from the input shaft 13. Next, when the sleeve 29 is engaged with the gear 21 side via the synchronizing mechanism 30,
The main shaft 20 is directly connected to the input shaft 13, resulting in a forward movement state in the D or [)S range. On the other hand, when the sleeve 29 is reversely engaged with the gear 1722 side via the synchro mechanism 31, the input shaft 13 is connected to the main shaft 20 via the gears 21, 24, 26, 22, the engine power is decelerated and reversed, and the R The range moves backwards.

In the boolean ratio conversion unit 4, a sub-shaft 35 is arranged parallel to the main shaft 20, a main pulley 3G and a sub-pulley 37 are provided on both shafts 20.35, respectively, and both boules 6-36. Between 37 and 37, the drive bells 1 to 34 of the kingless ring are hung. Both of the pulleys 36 and 37 are divided into two parts, one of which is one-way half-rest 36a, 37a,
The other half of the pulleys 36b and 37b are made freely movable f11i with variable intervals between the pulleys 36b and 37b on the moving side pulley half 36.
11.37+1 is equipped with a hydraulic servo device 38, 39 which also serves as a piston, and a spring 40 is attached to the movable bobber half 371 of the auxiliary pulley 37 in the direction of narrowing the pulley interval. Forced.

Further, an A-il pump 41 serving as an operating source is installed next to the main pulley 36 as a hydraulic control system. This Aile pump 41
is a gear pump for high pressure, and the pump drive #JI ft
42 is directly connected to the crankshaft 10 through the soil pulley 36, the main shaft 20, and the input shaft 13, and is designed to generate hydraulic pressure during engine operation. Then, C1 controls the hydraulic pressure of this oil pump 41 and each hydraulic servo i4@38.3
9, and changed the spacing between the main pulley 36 and the 1st pulley 37 to the opposite relationship, and made the pulley ratio of the drive belt 4 (36 and 37) stepless. Transmission (), outputs continuously variable power to the subshaft 3.

In view of the fact that the minimum pulley ratio on the high-speed stage side of the pulley converter 4 is very small, for example, 0.5, and the rotation speed of the LC subshaft 35 is too large, the final reduction unit 5 is A C output shaft 44 is connected via a 1-phase intermediate reduction gear 43.43''. A flute initial gear 46 meshes with a drive gear 45 of this output shaft 44, and a final gear V 46 is connected via a differential mechanism 47. The power is transmitted to the axles 48 and 49 of the left and right drive shafts.

In the drawings after Figure 2, the stepless variable 3i tm 2
Explaining the lubricating device for the belt and boob parts,
As shown in Fig. 3, main pulley 3G and sub pulley 37J:
Volume 1-34 (=t i:J bell 1-34)
Since two small spaces s and s'' are formed facing each other between the two, the lower space S of these is filled with 11 nos'.
50 is attached. Also, although not shown in FIGS. 1 and 2, the pulley conversion section 4 of the main case 7 and the switching section 3 J
5 and the gear A7 section of the final reduction section 5, a hole 71) is provided at the location where the hydraulic rib system @39 of one of the sub pulleys 37 enters the gear section side.
Since the partition wall 7C is formed around 1), the partition wall 7C is used to position the refueling nozzle 50.
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That is, as shown in FIG. 4, the refueling nozzle 50 has a large diameter portion j]
An elongated cylindrical body 52 is connected to one side of 1, and a large diameter portion 51
Two legs 53 are erected in the shape of a letter around the cylindrical body 52, and a large diameter portion 53 and a passage 54 inside the cylindrical body 52 communicate with an ejection hole 55 at the tip of the cylindrical body 52. Therefore, as shown in Figure 2,
By inserting the cylindrical body 52 of the refueling nozzle 50 from the gear part side of the main case wall 7a, touching the two legs 53 to the partition wall 7C, and pressing the rear part of the large diameter part 51 so that it does not slip out, The refueling nozzle 50 is positioned and fixed,
In this state, the oil vibrator 5G is press-fitted into the passage 54 of the large diameter portion 51 and connected thereto.

On the other hand, the jet hole 55 at the tip of the cylindrical body 52 is now connected to the belt 3.
It is located approximately at the center of the width of 4. Here, the belt 34 is the third
Shown in the figure? lJ, the direction of rotation is U, and the leading side of this bell 1 in the rotation direction is one of the sub pulleys 31.1) t
The direction of the ejection hole 55 is the minimum diameter part 3 of the sub pulley 37.
The tangent line to 7C is set.

Next, the operation of the lubricating device constructed as shown in J.
9 = When the vehicle is running, the engine movement input to the main shaft 20 via the switching unit 3 is controlled by the main pulley 3G and sub pulley 3 by the hydraulic servo device 38.39.
7 and the belt 34, the speed is continuously variable and taken out to the subshaft 35. At the start of running, the belts 1 to 34 are in the low speed stage where the secondary pulley 37 is wrapped as shown in FIGS.
The belt 34 is wound around the minimum diameter portion 37c of the sub pulley as shown by the dashed line in FIG. 3, and the gear ratio becomes the minimum in the lζ state.

Therefore, bell 1-34 and main pulley 3G as shown in J above.

When the sub pulley 37 rotates and performs a speed change operation, oil is injected from the jet hole 55 of the oil supply nozzle 50.
Along the rotational direction of the belt 34, and because the sub pulley 37 restricts the oil to the point where the bending movement of the belt 34 is greatest, the oil is drawn inside by the bending movement of the belt 34 and can remain there for a long time. Thus belt 3
4 itself, as well as the contact area between it and the sub pulley 37,
Even in the lower main pulley 36, the contact parts of the 10-Δ-Y lever, J and the liber l-34, which are brought into contact with each other, are sufficiently lubricated. Historically, high-speed stages in which the bell 1 (34) was wound around the smallest diameter portion (37) of the sub-pulley (37) were frequently used.
Nowadays, the smallest diameter part 3700 of the subboot generates the most heat, and the oil from the spout hole 55 directly flows into this part.
If it is shot once, it will effectively be cold fJI.

It should be noted that the present invention is not limited to the above-mentioned embodiments.
-1: Oil can also be directly injected to the booby side.

As is clear from the example 1- below, according to the present invention,
In the continuously variable transmission 2, the inside of the belt is supplied with oil in the space between the belt 34, the main pulley 36, and the sub pulley 37. ~Inside oil supply system is easy 141, t-1
be sure to be configured. Spout hole ti J of refueling nozzle 50
The oil from the bell 1 is injected in the two tangential directions from the smallest diameter part of the pulley on the advancing side of the rotational direction, so the lubrication effect is very large.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional view showing an example of a continuously variable transmission to which the present invention is applied, FIG. 2 is a cross-sectional view taken along the line ■-■ in FIG. Figure 3 is l-1f of Figure 1.
FIG. 4 is a perspective view of the oil supply nozzle. 2...Continuously variable transmission, 4...Pulley ratio conversion section, 7...
・Main case, 7a... Wall, 71]... Hole, 7
G... A1 cut wall, 34... Drive bell h, 36...
Main pulley, 37... Sub-pulley, 37c... Minimum diameter part, 50... Supply h1+ nozzle, 55... Spout hole, S,
S-...Space. Patent applicant Tomiju Heavy Industries Co., Ltd. agent Patent attorney Kobashi Example Float valve I! I! =Susumu Murai

Claims (1)

[Claims] A pair of pulleys where the ratio of the winding iJ diameter changes η are wound around (
) A refueling nozzle is positioned and fixed in the space between the bell and the bell, and the direction of the jet hole of the refueling nozzle is set in the space between the bell L and the pulley on the forward side in the rotational direction. A lubricating device for a continuously variable transmission characterized by being set to be tangent to the minimum (¥ part).