JP2559353Y2 - Fluid retarder device - Google Patents

Description

[Detailed description of the invention]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fluid type retarder device.

[0002]

2. Description of the Related Art There are known large vehicles such as trucks and buses equipped with a hydraulic retarder device. The fluid type retarder device generates braking torque when descending a slope, decelerating from a high speed, or the like, prevents fade due to a rise in brake temperature, and improves vehicle safety and durability of friction materials.

[0003] As a conventional fluid type retarder device, there is one disclosed in, for example, Japanese Patent Application Laid-Open No. 63-30695.
This fluid type retarder device has a structure in which a clutch device is arranged outside a case, and a cylinder device which is a driving device for connecting and driving the clutch device is arranged outside the case. Such a hydraulic retarder device includes a rotor that can be fixed to a rotating shaft that rotates together with wheels such as a propeller shaft, and a stator that is fixed to the vehicle body so as not to rotate, and the rotor is rotated by a clutch device. And a braking torque is generated by the velocity energy of the working fluid between the stator and the rotor. The case accommodating the stator and the rotor is always filled with a fluid.

According to this fluid type retarder, since the clutch device is disposed outside the case, the internal space of the case accommodating the stator and the rotor can be reduced. In addition to not being able to obtain the function, there are many rotating slide portions between the working fluid in the case and the outside air outside the case, and the fluid is likely to leak. In addition, since a relatively sharp peak torque value is generated immediately after the start of the operation of connecting the clutch device to operate the fluid type retarder device, a connection shock occurs, and the braking feeling given to the occupant is unpleasant. In order to promote the wear of the friction material of the clutch device, a large-sized clutch device is required, which is inferior in durability.

[0005]

SUMMARY OF THE INVENTION The present invention has been made in view of such a conventional technical problem, and has a rotor which can be fixed to a rotating shaft which rotates together with a wheel so that the rotor cannot rotate relative to the rotating shaft. And a stator provided opposite to the rotor and fixed to the vehicle body side member, and a clutch device capable of connecting and disconnecting the rotating shaft and the rotor. The clutch device is fixed to the rotor, and a plurality of pressure devices are provided. A support member movably supporting the plate in the axial direction of the rotary shaft and rotatably supported by the case, and a clutch disposed between the pressure plate and movably supported in the axial direction by the rotary shaft side member. A hydraulic retarder device having a plate, wherein the rotor, the stator, and the clutch device are filled with a working fluid and housed in a case fixed to a vehicle body-side member, and are circumferentially spaced. A plunger member is provided to penetrate the case in a liquid-tight and slidable manner, and presses a pressure plate located at an end of the support member.The plunger member is disposed outside the case, and the plunger member is pressed and driven toward the inside of the case. And a drive device for connecting a clutch device, wherein the plunger member is divided into a pressure plate-side member and a drive device-side member, and a compressible elastic body is interposed therebetween. It is a retarder device.

[Action]

[0006] Such a hydraulic retarder device obtains a braking torque by driving a driving device and connecting and operating a clutch device while the vehicle is running. That is, by driving the driving device, the plunger member is pressed and driven toward the inside of the case, and the pressure plate located at the end is pushed in, so that the clutch plates are pinched between the pressure plates, and the clutch device is connected. The rotor starts rotating via the rotating shaft, the clutch plate, each pressure plate, and the support member. As a result, the function of the retarder device is exhibited, and the velocity energy of the working fluid generated by stirring by the rotor is absorbed as heat into the working fluid via the stator. As described above, the operation of the hydraulic retarder device is performed by only the plunger member protruding into the case.

Immediately after the operation of such a fluid-filled type hydraulic retarder apparatus starts, immediately after the plunger member starts sliding, the elastic body can be compressed and deformed.
Each pressure plate is prevented from strongly pressing the clutch plate, and a pressing force corresponding to the elastic force of the elastic body is obtained. That is, until the elastic body is sufficiently compressed and deformed, the length of the elastic body in the sliding direction is gradually reduced while the elastic body is gradually compressed and deformed, and after the elastic body is sufficiently compressed and deformed, both are used as plunger members. By sliding together, the clutch device is completely connected, and the pressure plates and the clutch plates are strongly pinched to rotate integrally. Until the clutch device is connected,
The rising speed of the rotation speed of the rotor is reduced according to the amount of elastic deformation of the elastic body.

As a result, the improvement of the braking torque rising characteristic can be obtained as follows. That is, of the generated torque, the peak torque value generated by suddenly rising due to the start of stirring of the working fluid immediately after the start of braking is significantly reduced, and thereafter, a steady curve having a substantially flat characteristic is drawn by drawing a gentle curve. To a typical set torque value. Thus, in a state where the working fluid, which also serves as cooling, circulates in the case by the self-pumping action of the rotor or the separate pump, the rotational energy of the rotor is transmitted as heat to the working fluid via the stator, and the deceleration action is performed. Occur. At this time, the clutch device is also cooled by the working fluid. Since the driving device is provided outside the case, no actual harm is caused by leakage of the working fluid such as the pressurized air.

When the drive of the fluid type retarder device is stopped, the drive of the drive device is stopped and the plunger member is returned. Thereby, the clutch device is disconnected and the rotation of the rotor is stopped. As a result, the velocity energy of the working fluid does not act on the stator, and the operation of the retarder device stops. Further, with the return operation of the driving device, the compressed state of the elastic body is also released, and the pressure plate side member and the driving device side member of the plunger extend, and return to the original position.

【Example】

An embodiment of the present invention will be described below with reference to the drawings. 1 to 5 show one embodiment of the present invention. As shown in FIG. 1, the fluid type retarder device includes a stator 5 and a rotor side case 1 and a stator side case 2 which will be described later.
The case 3 is integrally fixed with a plurality of hexagon socket head bolts 30b with the outward flange portion 5a and a seal ring (not shown) interposed therebetween. The case 3 is fixed to a vehicle body side member such as a transmission rear cover (not shown) and is non-rotating. At the center of the rotor-side case 1 and the stator-side case 2, a rotating shaft 10 such as a transmission output shaft is provided with two sets of seal members 31 and 32 and a bearing 3.
3, 34 and penetrate freely and liquid-tightly. The rotating shaft 10 is connected to wheels via a propeller shaft (not shown) or the like, and rotates with the wheels.
The sub rotary shaft 10b is serrated and connected to the main rotary shaft 10a, and is fixed with a nut 10c. 10d is a seal ring.

In this manner, the retarder chamber 4 is defined around the rotary shaft 10 by the case 3 with the seal members 31 and 32 interposed therebetween, and is always filled with the working fluid (oil or water).
Is defined. In the retarder chamber 4, a stator 5 having radial blades around the rotation shaft 10 is provided inside the stator-side case 2, and is positioned inside the rotor-side case 1. , Rotating shaft 10
And a rotor 6 having radial blades centered at the center and fixed to a member on the rotating shaft 10 side facing the stator 5 so as to be relatively non-rotatable. Thus, the stator 5 is integrated with the case 3 by the outward flange portion 5a, and is fixed to the vehicle body side member so as to be substantially non-rotatable.

Further, a working fluid inlet 9a is provided in the stator side case 2 located above the retarder chamber 4, and a working fluid outlet 9b is provided in the rotor side case 1 located above the retarder chamber 4. Further, a plurality of annular pressure plates 14 are provided on the inner peripheral portion of the rotor 6.
a, 14b... are spline-coupled to each other so as to be slidably supported in the center axis direction. The support member 7 is attached to the case 3 via the first bearing 12 and the second bearing 11. It is rotatably supported. That is, the first bearing 12 is provided by press-fitting and fixing the inner ring 12a to the annular step surface of the rotor-side case 1, and holds the rolling element between the inner ring 12a and the outer ring 12b. Is fixedly press-fitted to an annular step surface of a movable pressure plate 14a located at a position indicated by reference numeral 2, and holds a rolling element between itself and the outer ring 11b. One end of the support member 7 in the axial direction is press-fitted and fixed to the first cylindrical portion 15a of the pressure plate 15 which cannot be moved in the axial direction, and the first bearing is mounted on the second cylindrical portion 15b of the pressure plate 15. Twelve outer rings 12b are press-fitted and fixed.

The outer race 11b of the second bearing 11 is press-fitted and fixed to an annular step surface of a ring-shaped connecting member 20, and a plunger member 21 described later is fixed to an outer peripheral portion of the connecting member 20. Thus, one end of the support member 7 that supports the rotor 6 has the pressure plate 15 and the first
Pressure plate 1 rotatably positively supported by rotor side case 1 via bearing 12 and having a movable other end.
4a, the second bearing 11, the connecting member 20, and the plunger member 21 rotatably supported by the stator side case 2.

On the other hand, a plurality of clutch plates 16
The pressure plates 14a, 14b,... Are arranged on the spline teeth 10e of the rotary shaft 10 so as to be movable in the axial direction.
・ It is sandwiched between 15. The support member 7, the pressure plates 14a, 14b,..., 15, the clutch plate 16 and the like constitute a clutch device 13 capable of connecting and disconnecting the rotary shaft 10 side member and the rotor 6. Thus, the clutch plate 16 that rotates integrally with the rotating shaft 10
, The pressure plates 14a, 14b,.
5, the clutch device 13 is connected, and the cylindrical support member 7 rotatably supported by the case 3, which is a non-rotating portion, via the first bearing 12 and the second bearing 11.
Rotate, the rotor 6 integrated with the support member 7 rotates integrally with the rotating shaft 10.

Next, the plunger member 21 and the driving device 22 for connecting and driving the clutch device 13 will be described.
The plunger member 21 is provided so as to penetrate the stator-side case 2 in a liquid-tight and slidable manner at intervals in the circumferential direction, and has one end coupled to the outer ring 11 b of the second bearing 11 via the connecting member 20. Reference numeral 23 denotes a seal ring for maintaining liquid tightness between the plunger member 21 and the stator side case 2. As shown in detail in FIG. 2, the plunger member 21 is divided into a pressure plate side member 35 and a drive device side member 36, and a compressible elastic spring 37 is interposed between the two. Is done.

More specifically, a driving device side member 36 also having a bottomed cylindrical shape is slidably inserted into a pressure plate side member 35 having a bottomed cylindrical shape. Is engaged with the inwardly protruding portion 35a at the other end of the pressure plate-side member 35, so that the separation of the two 35 and 36 is prevented. During the connection operation of the plunger member 21, the spring 37 compresses and deforms until both ends of the outwardly projecting portion 36 a of the drive device side member 36 abut on the bottom of the pressure plate side member 35.
6 gradually decreases in the sliding direction, and the outward projection 3
After one end of 6a comes into contact with the bottom of the pressure plate side member 35, both 35 and 36 slide together. It should be noted that three or more plunger members 21 are provided in the circumferential direction of the annular connection member 20.

The drive unit 22 is disposed outside the case 3, that is, outside the stator side case 2, and is integrally fixed to the stator side case 2 by bolts 30 a so as to cover the outer peripheral portion of the stator side case 2. 24, and a piston member 25 disposed between the stator side case 2 and the cover 24. The inner peripheral portion of the piston member 25 is fixed to the plunger member 21, that is, the other end of the driving device side member 36, and the annular stepped surface 25 a protruding in a cylindrical shape is formed on the annular inner peripheral surface of the cover 24 via the seal member 26. 24a is slidably fitted. Further, an outer peripheral portion of the piston member 25 is bonded to an inner peripheral portion of a diaphragm 27 having airtightness and flexibility, and an outer peripheral portion of the diaphragm 27 is sandwiched between the stator side case 2 and the cover 24. I have.

Thus, the stator-side case 2 and the cover 2
4, between the piston member 25 and the diaphragm 27
A pressure chamber 29 is defined thereby. This pressure chamber 29
Is connected to a pressure air supply source via a switching valve (not shown) so that pressure air can be supplied or drained to the pressure chamber 29 by switching operation of the switching valve. When the pressure chamber 29 is drained, the piston member 25 is returned to the other end by, for example, a return spring (not shown) compressed and interposed between the stator side case 2 and the piston member 25. Will be

Next, the operation of the fluid type retarder will be described. While the vehicle is running, a retarder switch (not shown) is turned ON to drive the drive device 22 to connect and operate the clutch device 13. That is, pressurized air is supplied to the pressure chamber 29 from the outside, and the piston member 25 is slid leftward in FIG. 1 to push the plunger member 21 and the connecting member 20. At that time, the diaphragm 27 is deformed. As a result, the pressure plate 14a is pushed in through the second bearing 11, and each pressure plate 14a is pressed.
a, 14b..., 15, each clutch plate 16 is pinched and the clutch device 13 is connected.
0, each clutch plate 16, each pressure plate 1
The rotor 6 starts rotating via the support members 7 and 4a, 14b,... In this way, the function of the retarder is exhibited, but the operation of the fluid retarder is
Only the plunger member 21 protrudes into the case 3.

Immediately after the operation of such a fluid-filled type hydraulic retarder apparatus starts, immediately after the piston member 25 starts sliding to the left, the spring 37 of the plunger member 21 can be compressed and deformed. The plates 14a, 14b,..., 15 are prevented from strongly pressing each clutch plate 16, and the springs 37
Squeezing pressure corresponding to the resilience of the spring is obtained. That is, until one end of the outwardly protruding portion 36a of the driving device side member 36 contacts the bottom of the pressure plate side member 35, the length of the two members 35, 36 in the sliding direction gradually decreases while the spring 37 is compressed and deformed. After one end of the outwardly projecting portion 36a contacts the bottom of the pressure plate-side member 35 and the spring 37 is sufficiently compressed, the two members 35 and 36 slide together to form the respective pressure plates 14a and 14a.
, 15 and each clutch plate 16 are strongly pressed to rotate integrally.

FIG. 3 shows the relationship between the lapse of time after the start of driving of the driving device 22 and the axial pressing force generated on each of the pressure plates 14a, 14b,. As is known from the figure, in the case of the conventional product indicated by a broken line B (the plunger member 21 is formed integrally and does not have the spring 37), the axial pressing force is made to be linear with time. And reaches the connection load X of the clutch device 13, but according to the product of this embodiment indicated by the solid line A, immediately after the start of driving, an axial pressing force corresponding to the elastic deformation of the spring 37 is obtained, and After the device-side member 36 comes into contact with the pressure plate-side member 35 and reaches the break point a, the driving force of the driving device 22 reliably acts on the connecting member 20, and the connection force X of the clutch device 13 is reached. Reach.

The relationship between the lapse of time after the start of driving of the driving device 22 and the rotation speed of the rotor 6 is as shown in FIG.
In the state where the rotating shaft 10 rotates at 3000 rpm, in the case of the conventional product indicated by the broken line B, the rotational speed rapidly increases immediately after the start of driving, and then reaches the connection completion point b of the clutch device 13. According to the product of the present embodiment indicated by the solid line A, immediately after the start of driving, the speed of increase of the rotation speed is moderated according to the elastic deformation of the spring 37, and the speed is gradually obtained. Reach

As a result, the improvement of the braking torque rise characteristic is obtained as follows. That is, in FIG. 5, the solid line A shows the characteristics of the product of the present embodiment, and the broken line B shows the characteristics of the conventional product. According to the product of the present embodiment, as is known from the figure, the peak torque value d of the conventional product, which is generated by abruptly rising due to the start of stirring of the working fluid immediately after the start of braking, out of the generated torque, It is remarkably reduced to the peak torque value e, and then converges to a steady set torque value f having a substantially flat characteristic with a gentle curve. The set torque value f is not different between the conventional product and the product of the present embodiment.

As described above, the function of the retarder device is exerted, and the velocity energy of the working fluid generated by the stirring by the rotor 6 is absorbed. That is, in a circulating state in which the working fluid also serving as cooling flows in from the working fluid inlet 9a and flows out from the working fluid outlet 9b by the self-pumping action of the rotor 6 or the electric separate pump, the rotational energy of the rotor 6 is increased. Is transmitted to the working fluid as heat, and a deceleration action occurs. At this time, the clutch device 13 is also cooled by the working fluid. In addition, since the drive device 22 is provided outside the case 3, there is no actual harm caused by leakage of the compressed air.

When the retarder switch is turned off, the pressurized air in the pressure chamber 29 is drained, and the drive of the retarder device stops. That is, the piston member 25, the plunger member 21, the connecting member 20, and the second bearing 11 are returned by the resilience of a return spring (not shown), and the clutch device 13
Is cut off, so that the rotation of the rotor 6 stops. As a result, the speed energy of the working fluid does not act on the stator 5, and the operation of the retarder device stops. With the return operation of the piston member 25, the compressed state of the spring 37 is released, and the pressure plate side member 35 and the drive device side member 36 of the plunger member 21 extend, and return to the original position. In the return state of the plunger member 21, the outwardly protruding portion 36a of the drive device side member 36 and the inwardly protruding portion 35a of the pressure plate side member 35 are engaged, thereby preventing the two 35, 36 from separating and falling off. In addition, both projecting portions 3
Since the engagement of 5a and 36a prevents separation of the two 35 and 36, the spring 37 can be given a slight initial compression to be interposed between the two 35 and 36.

The first bearing 12 only needs to rotatably support the support member 7 on the case 3. The inner ring 12a of the first bearing 12 is fixed to the pressure plate 15 so as not to move in the axial direction, and the first bearing 12 is fixed to the outer ring. 12b can be fixed to the rotor side case 1. The same effect can be obtained by fixing the inner ring 11a of the second bearing 11 to the connecting member 20 and fixing the outer ring 11b to the movable pressure plate 14a located at the end. Further, the connection member 20 is omitted, and the inner ring 11a or the outer ring 1 of the second bearing 11 is omitted.
1b may be directly fixed to the pressure plate side member 35 of the plunger member 21.

[Effect of the invention]

As will be understood from the above description, the following effects can be obtained by the hydraulic retarder according to the present invention. (1) Since the plunger member only protrudes into the case during the connection operation of the clutch device, the change in the internal volume of the case is small, and a pressure increase that occurs temporarily immediately after the start of operation can be suppressed. In addition, at the time of the connection operation of the clutch device, the elastic body is elastically compressed and deformed, thereby preventing a sudden connection operation. As a result, the braking torque generated by the hydraulic retarder device can be stably obtained. (2) Since the clutch device is disposed inside the case and the drive device for connecting and disconnecting the clutch device is disposed outside the case, the case accommodating the stator and the rotor while obtaining the cooling action by the working fluid of the clutch device. Internal space can be reduced.

(3) Since the driving device can be disposed outside the case with a reduced number of rotating slides for maintaining liquid tightness in the case, leakage of the working fluid can be prevented well. (4) Since the drive device is disposed outside the case, maintenance and inspection are easier than when the drive device is disposed inside the case.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a half part of a hydraulic retarder device according to an embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing a main part of the same.

FIG. 3 is a diagram showing time-axial direction pressing force characteristics.

FIG. 4 is a diagram showing time-rotor rotation speed characteristics.

FIG. 5 is a diagram showing time-generated torque characteristics.

[Explanation of symbols]

1: rotor-side case, 2: stator-side case, 3: case, 4: retarder chamber, 5: stator, 6: rotor, 7:
Support member, 9a: working fluid inlet, 9b: working fluid outlet,
10: rotating shaft, 11: second bearing, 11a: inner ring, 11
b: outer ring, 12: first bearing, 12a: inner ring, 12b: outer ring, 13: clutch device, 14a, 14b, 15: pressure plate, 16: clutch plate, 20: connecting member, 21: plunger member, 22: drive Apparatus, 23:
Seal ring, 24: cover, 25: piston member, 2
6: sealing material, 27: diaphragm, 29: pressure chamber, 3
1, 32: seal member, 33, 34: bearing, 35: pressure plate side member, 35a: inward projecting portion, 36:
Drive device side member, 36a: outward protruding portion, 37: spring (elastic body).

Claims (1)

(57) [Scope of request for utility model registration] 1. A rotor which can be fixed to a rotating shaft that rotates together with wheels so as to be relatively non-rotatable, a stator provided opposite to the rotor and fixed to a vehicle body side member, and a rotating shaft and a rotor can be connected and disconnected A supporting member fixed to the rotor, supporting the plurality of pressure plates movably in the axial direction of the rotating shaft and rotatably supported by the case, and the pressure plate. And a clutch plate supported by the rotating shaft side member so as to be movable in the axial direction. The rotor, the stator, and the clutch device are filled in a working fluid and housed in a case fixed to the vehicle body side member. And a pressure plate disposed at an end of the support member, the case being provided so as to penetrate the case in a liquid-tight and slidable manner at intervals in a circumferential direction. A plunger member for pushing the plunger member, a driving device for pressing the plunger member into the case and driving the plunger member to connect the clutch device, and the plunger member is a pressure plate side member and a driving device. A fluid type retarder device, wherein the fluid type retarder device is divided into two parts and a side member, and a compressible elastic body is interposed between the two.