JPH038816Y2 - - Google Patents

Description

[Detailed Description of the Invention] [Technical Field of the Invention] This invention relates to a lubricating device for a wet multi-plate clutch in a press machine.

[Technical background of the invention and its problems] In general, in wet multi-disc clutch brakes, it is important to reliably supply an appropriate amount of lubricating oil to the surfaces of the friction plates.
It is necessary to suppress heat generation and wear and maintain performance.

Conventionally, two types of lubrication systems have been used for wet multi-disc brakes: an oil bath type and a forced circulation type. The oil bath lubrication system stores lubricating oil to a certain required level in the casing that houses the clutch brake, and lubricates the necessary parts like an oil bath. In addition, in the forced circulation lubrication system, a separate oil pump unit is installed, and lubricating oil is pumped to the clutch brake section through piping connections to lubricate the necessary areas, and the returned oil is collected from the casing back into the oil pump unit. be.

Press machines using wet multi-disc clutch brakes employ oil bath lubrication mainly in relatively small capacity press machines because they do not require a separate oil pump unit. Press machines that employ a forced circulation lubrication system have relatively large capacities and require harsh clutches.

However, in conventional press machines equipped with wet multi-disc clutch lubrication systems, the lubrication system can be switched between an oil bath lubrication system and a forced circulation lubrication system, making it possible to change the lubrication system according to the application with a single machine. However, nothing that can be used for presses in many areas has yet to be found.

[Purpose of the invention] This invention was made in view of these conventional problems, and it allows easy switching between the oil bath lubrication system and the forced circulation lubrication system, making it possible to improve press working in various fields. It is an object of the present invention to provide a lubrication device for a wet multi-disc clutch that can correspond to the following.

[Summary of the invention] This invention is a wet multi-disc clutch brake with a built-in planetary gear device, in which a lubricating oil passage is provided on the input shaft and the output shaft, and the oil passage on the input shaft and the oil passage on the output shaft are communicated. The present invention is a wet type multi-disc clutch lubrication system characterized by the following features: By connecting to an external oil pump unit, it is possible to easily switch from an oil bath type lubrication system to a forced circulation type lubrication system.

[Embodiment of the invention] FIG. 1 shows a schematic front view of a press machine 1 equipped with a wet multi-disc clutch lubrication device according to an embodiment of the invention. 5 is tiltably supported. An eccentric shaft 7 is rotatably attached to the C-shaped frame 5, and an upper part of a connecting rod 9 is fitted onto the eccentric shaft 7. A ram 11 is pivotally attached to the lower part of the connecting rod 9.
Therefore, by rotating the eccentric shaft 7, the ram 11 is raised and lowered via the connecting rod 9. The eccentric shaft 7 is a C-shaped frame 5
The drive motor 13 inside is the driving force, and the clutch brake unit 15 and drive unit 17, which will be described later, are
It is rotationally driven through the.

To explain this drive system in more detail based on FIG. 2, the rotation of the motor 13 and motor pulley 19 is transmitted to the flywheel 23 of the clutch brake unit 15 by a V-belt 21.

As will be described later, the rotational force of the flywheel 23 is transmitted to the output shaft 25 of the clutch brake unit 15 by connecting and disengaging the clutch. The output shaft 25 in the drive unit 17 is directly connected to the eccentric shaft 7 by a gear coupling 27.

This gear coupling 27 has two gear meshing portions 27a and 27b on the left and right, and has flexibility due to a specially shaped crowning. Therefore, the impact bending force of the press eccentric shaft 7 is applied to the clutch output shaft 25.
Only the rotational torque is transmitted.

Therefore, when the clutch is connected within the clutch brake unit 15, the clutch output shaft 25 and the eccentric shaft 7 rotate, and the press ram 11 is slid.

Next, the internal structure of the clutch brake unit 15 will be explained in detail with reference to FIG. 3, and an embodiment of the wet type multi-disc clutch lubrication system employed in the clutch brake unit 15 will also be explained. In addition, generally the flywheel, clutch,
In the case of a press machine that is directly connected to an eccentric shaft and driven at the same rotational speed, its torque capacity is small, so it is used for machining with a short pressurizing distance, and therefore machining that requires small torque and energy capacity. However, in the case of a press machine equipped with a wet multi-disc brake with a built-in planetary gear reduction mechanism, such as the embodiment of this invention, it is possible to achieve quiet operation, low inertia, etc. It is possible to improve torque and energy capacity without sacrificing the advantages of the wheel direct connection type, which has the advantage of expanding the practical range.

Each mechanical component is housed within a casing 29 for mounting the entire clutch brake unit 15 within the C-shaped frame 5 in a wall-mounted manner. Flywheel support 31 for this casing 29
is fixed, and the flywheel support 31
On the other hand, the flywheel 23 is
It is pivotally supported via 3. Further, an input shaft 35 is rotatably inserted into the flywheel support 31 and is fixed integrally with the flywheel 23 and the flywheel hub 37. A sun gear 39 is fixed to the tip of the input shaft 35.

Therefore, the rotational force transmitted from the drive motor 13 by the V-belt 21 is transmitted to the flywheel 23,
It is transmitted to the sun gear 39 via the flywheel hub 37 and the input shaft 35.

The output shaft 25 has a gear engagement portion 27a attached to its outer end, and is pivotally supported by a bearing 41 with respect to the casing 29. This output shaft 2
The inner end of the input shaft 35 is fitted onto the outer periphery of the input shaft 35, and an appropriate number of planetary gears 43 are rotatably attached to the outer periphery of this end via pins 45.

Further, a disc-shaped pressure plate 47 is fixed to the inner circumference of the casing 29, and an appropriate number of clutch friction plates 49 and brake friction plates 51 are arranged on both sides of the pressure plate 47. The spline parts 55 and 57 of the internal gear 53 and the output shaft 25 are connected to each other, so that rotational force can be transmitted and movement can be made freely in the axial direction. These clutch friction plates 4
9. A guide pin 59 is installed between the brake friction plates 51.
A steel disk 61 supported by is interposed. This guide pin 59 is connected to the casing 2
9, and both friction plates 4
A clutch plate 63 and a brake plate 65, which are arranged on both sides of 9 and 51, are slidably attached. The brake plate 65 is always urged toward the pressure plate 47 by a brake spring 67 attached to the casing. Further, the clutch plate 63 and the brake plate 65 are connected by bolts 69, and a space collar 71 maintains a constant distance between them.

A piston 73 is installed on the side of the clutch plate 63.
are in contact. This piston 73 is inserted into a cylinder portion 75 of the flywheel support 31, and can be driven in the axial direction by air supplied through an air supply port 77.

The internal gear 53 spline-coupled to the clutch friction plate 49 is arranged to mesh with the planetary gear 43, and a slinger disk 79 is fixed to the end surface thereof. A slinger disk 81 is also fixed to the inner end surface of the output shaft 25.
In this way, both slinger disks 79 and 81 are positioned in the oil chamber 83 within the casing 29.

An oil receiver 85 is provided above the oil chamber 83, and an oil reservoir 87 is formed above the cylinder portion 75. An oil pan 89 is also provided on the side surface of the flywheel support 31 on the flywheel 23 side. Further, the end face portion of the flywheel 23 is closed by a flywheel cover 91 for oil sealing.

The operation of the clutch brake unit 15 having the above structure will now be described.

A Input shaft system Flywheel 23-Flywheel hub 37
- Input shaft 35 - Sun gear 39 When the drive motor 13 rotates, the flywheel 23 connected by the V-belt 21 rotates, and the above-mentioned members integrated therewith rotate at the same rotational speed.

B. Clutch Friction Plate/Internal Gear System Clutch Friction Plate 49 - Internal Gear 53 When the clutch friction plate 49 is rotated, the spline-coupled internal gear 53 is rotated around the output shaft 25 .

C Output shaft system Planetary gear 43 - Planetary gear pin 45 - Output shaft 2
5. Brake friction plate 51 When the planetary gear 43 rotates due to the rotation of the sun gear 39 and revolves around the sun gear 39 by meshing with the internal gear 53, the output shaft 25 connected by the pin 45 also rotates. At the same time, this output shaft 25
The brake friction plate 51 that is spline-coupled with the brake member also rotates. Gear meshing part 2 at the end of the output shaft 25
7a transmits power to the gear meshing portion 27b of the eccentric shaft 7 through the gear coupling 27.

D Planetary gear mechanism system Sun gear 39 - Planetary gear 43 - Internal gear 53 The planetary gear mechanism constituting the reduction mechanism rotates the output shaft 25 relative to the input shaft 35 by meshing the gears described above.
decelerates the speed.

E Pressure plate pneumatics - Brake spring system Brake plate 65 - Brake side steel disk 61 - Pressure plate 47 - Clutch side steel disk 61 - Clutch plate 63 When the piston 73 is not driven, the pressing force of the brake spring 67 Therefore, the brake plate 65 moves rightward in FIG. It is fixed via the disc 61 and guide pin 59, and applies a brake to the output shaft 25.

Conversely, when air is supplied to the cylinder part 75 from the air supply port 77 and drives the piston 73 to the left,
The piston 73 presses the clutch plate 63 to the left, causing the clutch friction plate 49 to press against the steel disc 6.
Make frictional contact with 1. This clutch plate 63
Due to the movement of the brake spring 67, the brake plate 65 also moves to the left due to the space collar 71.
be moved against the force of As a result, the brake friction plate 51 separates from the steel disk 61, leaving the output shaft 25 free.

On the other hand, as the clutch friction plate 49 comes into frictional contact with the steel disk 61, the internal gear 53 is spline-coupled to the clutch friction plate 49.
is fixed to the casing 29 via a guide pin 59 and a steel disc 61. As a result, the planetary gear 43 meshing with the sun gear 39 revolves while meshing with the internal gear 53, and provides decelerated rotation to the output shaft 25.

Here, the rotation ratio of the output shaft 25 to the input shaft 35 when the clutch is connected by driving the piston 73 will be determined. As shown in FIG. 4, the rotation speed of the input shaft 35 is set to N ₁ rpm, and the rotation speed of the output shaft 25 is set to N ₂ rpm. Also, the number of teeth of the sun gear 39
Z ₁ , the number of teeth Z ₂ of the planetary gear 43, the rotation speed n ₂ rpm, the number of teeth Z ₃ of the internal gear 53, and the rotation speed n ₃ rpm.

As explained above, when the clutch is engaged, the internal gear 53 is fixed to the casing 29, and its rotational speed n ₃ =0.

The rotation speed N ₂ of the output shaft 25 is given by N ₂ =Z ₁ /Z ₁ +Z ₃ ·N ₁ .

Furthermore, the rotation speed n ₂ of the planetary gear 43 is given by n ₂ =-Z ₁ /Z ₁ +Z ₃ ·Z ₃ /Z ₂ ·N ₁ .

Therefore, as an example, Z ₁ = 20, Z ₂ = 16, Z ₃ =
52, the rotational speed N ₂ of the output shaft 25 is given by N ₂ ≒0.27778N ₁ and the rotational speed n ₂ of the planetary gear 43 is given by n ₂ ≒ −0.090278N ₁ . Therefore, when the clutch is connected, the output shaft 25 rotates in the same direction as the input shaft 35, and the rotation speed is reduced to about 1/3.6.

Further considering the torque, when the clutch rated torque Tc is assumed, the rotational torque T ₁ transmitted to the input shaft 35 is T ₁ =Z ¹ /Z ₃ ·Tc The rotational torque T ₂ transmitted to the output shaft 25 is It is given by the relationship T ₂ =2(Z ₁ +Z ₂ )/Z ₃ ·Tc. Therefore, when substituting the same numerical values as above, it is given as T ₁ ≒(1/2.6)Tc T ₂ ≒1.3846Tc.

Typically, the design reduction ratio is in the range of 3.5-4.0. The rotation speed of the eccentric shaft 7 during actual use is 100-200 rpm
As shown in the calculation example above, when the rotation of the eccentric shaft 7 is within this range, the number of rotations of the flywheel 23 and input shaft 35 N ₁ = 3.6 × (100-200)
=360-720rpm. Therefore, the flywheel 23 can be rotated at a fairly high speed, and even with a small diameter, the energy capacity can be sufficiently increased.

Furthermore, the torque amplification ratio is required to be in the range of 1.35-1.40 in design, but as can be seen in the calculation example above, compared to the normal flywheel direct drive type.
It can be seen that the torque amplified by 1.35-1.40 times is applied to the output shaft 25.

Next, the configuration of the lubrication system in the clutch brake unit 15 will be explained. As shown in FIG. 3, the flywheel support 31 has a casing 2
A fuel filler port P ₁ is provided which communicates with the oil chamber 83 of No. 9, and a fuel filler port P ₂ that communicates with the fuel filler port P 1 and reaches the input shaft 35 in the radial direction of the flywheel support 31 is provided _. . In the input shaft 35, a threaded pump part _P3 is formed which communicates with the oil filler port _P2 , and a oil filler port _P4 is formed that passes through the center in the axial direction, and the fitting part side with the output shaft 25 is formed with a screw pump part P3 that communicates with the oil filler port P2. It is open at the end.

In the output shaft 25, the oil supply port of the input shaft 35
A fuel filler port _P5 is provided in the axial direction to face _P4 , and further, fuel filler ports _P6 and _P7 are formed in the radial direction so as to communicate with the fuel filler port _P5 . In addition, an oil filler port _P8 is formed on this output shaft 25.
The oil supply port P ₆ is communicated with the oil groove portion 93a of the oil feed ring 93. The planetary gear pin 45 also has an oil supply port that communicates with the oil groove portion 93a.
P ₉ is formed and is designed to lubricate the inner peripheral portion of the planetary gear 43.

The arrangement for lubricating the clutch friction plate 49 and brake friction plate 51 is shown in detail in FIG.
The clutch friction plate 49 and the brake friction plate 51 are respectively engaged with the internal gear 53 and the output shaft 25 by involute spline coupling. The spline portions 55, 57 of the clutch friction plate 49 and the brake friction plate 51 have some of their teeth arranged approximately equally on the circumference, with an appropriate number of missing teeth 55a, 5.
It is said to be 7a. Then, when assembling the clutch friction plate 49 to the internal gear 53 and the brake friction plate 51 to the output shaft 25 by spline connection, the missing teeth 55a and 57a are aligned in the axial direction through all the friction plates. are assembled in the same phase. Therefore, the missing teeth 55a and 57a form one oil passage. This oil passage then comes to communicate with the oil supply port _P8 of the output shaft 25.

On the other hand, in the flywheel support 31,
Another fuel filler port P ₂₁ is formed in a different radial direction from the fuel filler port P ₂ and communicates with a fuel filler port P ₂₂ extending in the axial direction at the center of the flywheel support 31 . The other end of this oil filler port P ₂₂ communicates with a bearing 33 of the flywheel 23.

The flywheel support 31 further includes an oil filler port P ₂₃ that communicates with the clearance with the input shaft 35, an oil filler port P ₂₄ that communicates with the oil pan 89, and this oil filler port.
An oil filler port P ₂₅ is formed that communicates P ₂₄ with the oil chamber 83.

As mentioned above, the inside of this clutch brake unit 15 is lubricated using the oil supply ports formed in each member. For this lubrication method, both an oil bath lubrication method and a forced circulation lubrication method can be selectively adopted.

If the capacity of the press machine is not required to be very large, an oil bath lubrication method is used. The formation of the oil supply path in this case is as follows.

As shown in FIG. 3, the opening of the fuel filler port _P2 is closed with plugs _G1 and _G2, respectively. Also, fuel filler port P ₂₅
are closed by plugs G ₃ , G ₄ , and G ₅ . Furthermore, the oil filler port for bearing lubrication of the flywheel 23
P ₂₁ is also blocked by plug G ₆ and cannot be used as a refueling port.

Also, in the casing 29 (not shown), the oil chamber 8
The return oil port for connecting No. 3 to external piping is closed.

With this configuration, the oil supply path in the oil bath lubrication system is as follows. The lubricating oil is introduced into the oil chamber 83 up to the level of the shaft center of the output shaft 25 or to a level slightly lower than the shaft center.

When the drive motor 13 is driven and the flywheel 23 on which the V-belt 21 is hooked and the input shaft 35 are simultaneously driven, if the clutch is in the disengaged state, the internal gear 53 and clutch friction plate 49 operate the planetary gear mechanism. The flywheel rotates in the opposite direction to the input shaft system at a slightly reduced speed. Further, the slinger disk 79 fixed to the internal gear 53 also rotates at the same time, and the oil chamber 83 is
Splash the oil inside upwards.

On the other hand, when the clutch is in the connected state, the internal gear and clutch friction plate system are fixed, and the output shaft 25,
The output shaft system, such as the brake friction plate 51, rotates in the same direction at a slower speed than the input shaft system via the planetary gear mechanism. Therefore, another slinger disk 81 fixed to the output shaft 25 also rotates at the same time, and its outer peripheral blade portion splashes the oil in the oil chamber 83 upward.

In this way, oil is splashed up by either one of the slinger discs 79, 81 whether the clutch is in the engaged state or in the disengaged state.
The splashed oil hits the oil pan 85 and is collected in an oil reservoir 87 outside the cylinder portion 75 of the flywheel support 31. The oil in this oil reservoir 87 is guided to the threaded pump portion P ₃ of the input shaft 35 through oil supply ports P ₁ and P ₂ communicating therewith.

The input shaft 35 is rotating, and the lubricating oil introduced thereto is forced into the oil supply port _P4 .

The oil sent to the oil filler port P ₄ is guided to the oil filler port P ₅ of the output shaft 25, and is sent out from the oil filler ports P ₆ and P ₇ to the outer circumference of the shaft.

The oil from the oil filler port P ₆ passes through the oil groove 93a of the oil feed ring 93 and reaches the axial center oil filler port of the planetary gear pin 45.
The inner peripheral part of the planetary gear 43 is lubricated through _P9 . At the same time, oil from the oil groove portion 93a passes through yet another oil supply port _P8 of the output shaft 25 and is led to the vicinity of the clutch friction plate 49 and brake friction plate 51.

The oil that is sent to the vicinity of the clutch friction plate 49 and brake friction plate 51 flows through toothless portions 55a and 5 formed in the friction plates 49 and 51, as shown in FIG.
Each friction plate 49, 51 passes through the oil passage formed by 7a.
It lubricates the surface.

The oil passing through this friction plate part is pumped by the pressurizing force of the screw pump part _P3 of the input shaft 35, the pumping action of the lining oil groove of the idling side friction plate, and centrifugal force from the friction plate axis side in the outer radial direction. It passes through with appropriate pressure. As a result, the idling side friction plates are separated with a uniform gap maintained without touching each other, and effective rotation can be performed with less drag torque and therefore less heat generation.

The oil that has passed through this friction plate is returned to the oil chamber 8.
Returned to 3.

A small amount of oil supplied to the outer circumferential portion of the output shaft 25 from the oil supply port P ₇ is used to lubricate the bearing 41 portion.

The oil supply route when using the forced circulation lubrication method is as follows. In FIG. 3, the oil filler port formed in the radial direction of the flywheel support 31
Plug G ₁ at the outer peripheral opening of P ₂ is removed, and the opening is connected to the oil circulation pump by an external piping (not shown). On the other hand, the oil filler port _P1 is closed by a plug _G7 .

The plug _G6 of the oil supply port _P21 for lubrication on the input shaft 35 side is also removed to form an opening, to which external piping from the pump is connected.

Further, the plug _G5 of the oil filler port _P25 is removed to lubricate the input shaft 35 side, and the oil receiver 89 is made to communicate with the oil chamber 83.

In addition, in order to connect the external piping for sending the return oil to the pump unit, the return oil plug (not shown) provided in the opening that communicates with the oil chamber 83 is also removed and used as an opening to connect the return oil to the pump unit. Connect the oil external piping.

In this way, a forced circulation path is formed for the external pump unit, with the oil supply ports P ₂ and P ₂₁ serving as supply ports and the return oil port (not shown) of the oil chamber 83 serving as an oil drain port.

The oil supply route in the forced circulation lubrication system connected to piping in this way is as follows. The lubricating oil supplied from the oil filler port _P2 is the same as in the oil bath lubrication system: oil filler port _P2 - screw pump part P ₃ - oil filler port P ₄ - _{P 5} - P ₆ - oil groove part 93a - oil filler port P ₈ - Friction plate part - Oil chamber 83 - External pump unit.

The lubricating oil supply route on the input shaft 35 side is the oil filler port.
P ₂₁ -P ₂₂ are supplied to lubricate the bearing 33 portion. The oil from this bearing portion is collected in the oil receiver 89, sent to the oil supply ports P ₂₄ -P ₂₅ and the oil chamber 83, and sent to the external pump unit together with the lubricating oil on the output shaft 25 side.

[Effects of the invention] As can be understood from the description of the embodiments above, in the present invention, the screw pump part _P3 is provided on the input shaft 35 in the humidity type multi-disc clutch, so that the output shaft 25 can be stopped. Even in such a case, as long as the input shaft 35 is rotating, the lubricating oil is pumped, and lubrication can be ensured. In addition, the opening of the oil supply port formed to send lubricating oil to each friction part, etc. can be closed with a plug, and can be connected to an external pump unit if necessary. Because of this, it is also possible to forcibly lubricate with an external pump unit if necessary.

That is, in the present invention, it is possible to switch between the oil bath type lubrication system and the forced circulation type lubrication system.

[Brief explanation of the drawing]

Fig. 1 is a front view of a press machine using an embodiment of this invention, Fig. 2 is an enlarged front view showing the drive system of the press machine, and Fig. 3 is a clutch brake using an embodiment of this invention. Cross-sectional view of the unit,
FIG. 4 is a side view illustrating the operation of the clutch brake unit, and FIG. 5 is a side view showing a lubricating oil supply path to the friction plate portion of the clutch brake unit. 13... Drive motor, 15... Clutch brake unit, 17... Drive unit, 21... V
Belt, 23... flywheel, 25... output shaft, 29... casing, 31... flywheel support, 33... bearing, 35... input shaft, 37... flywheel hub, 39... sun gear, 41...Bearing, 43...Planetary gear,
45... Planet gear pin, 47... Pressure plate, 49... Clutch friction plate, 51... Brake friction plate, 53... Internal gear, 55, 57... Spline portion, 59... Guide pin, 61...Steel disk, 63...Clutch plate, 65
... Brake plate, 67 ... Brake spring,
69...Bolt, 71...Space color, 73
... Piston, 75 ... Cylinder section, 77 ... Air supply port, 79, 81 ... Slinger disc, 83 ...
...Oil chamber, 85...Oil pan, 87...Oil sump, 89...
...Oil pan, 91...Flywheel cover, 93...
Oil sending ring, 93a...Oil groove portion, P ₁ , P ₂ , P ₄ ,
P ₅ , P ₆ , P ₇ , P ₈ , P ₉ , P ₂₁ , P ₂₂ , P ₂₃ , P ₂₄ , P ₂₅
...Oil filler port, P ₃ ...Screw pump section, G ₁ , G ₂ , G ₃ ,
_G4 , _G5 , _G6 ...Plug.

Claims (1)

[Scope of utility model registration request] The flywheel support 31 attached to the casing 29 is provided with the flywheel 23 rotatably supported, and an input shaft 35 connected to the flywheel 23 is rotatably supported, and the input shaft 35 and the casing 29 are provided with a rotatable support. A clutch/brake mechanism housed in a casing 29 is connected to the freely supported output shaft 25, and a fuel filler port _P4 formed on the input shaft 35 and a fuel filler port _P5 formed on the output shaft 25 are connected to the freely supported output shaft 25. The clutch is connected to
The lubricating device is a wet type multi-disc clutch configured to supply lubricating oil to the brake mechanism and each friction part, and the input shaft 35 is provided with a screw pump part _P3 that pumps lubricating oil to the oil supply port _P4 , An oil supply port P ₂ that communicates with the oil supply port P ₁ that communicates with the oil reservoir 87 in the casing 29 to supply lubricating oil to the screw pump part P ₃ is provided so as to be able to communicate and be closed, and can be freely closed or closed by a plug G ₁ . A lubrication device for a wet multi-disc clutch, characterized in that it can be freely connected to an external pump unit.