JPH04117934U - torque transmission device - Google Patents

Abstract

(57) [Summary] [Purpose] Torque is transmitted between the two shafts due to the relative rotational speed difference between the input and output shafts, and the transmitted torque value is controlled according to the magnitude of the absolute rotational speed of these two shafts. The purpose is to [Structure] A first rotating member formed on one side of a relatively rotatable input/output shaft and having a cam surface on the inner circumference, and a second rotating member formed on the other side of the input/output shaft and inserted into the cam surface. a cam body that is supported by a second rotating member and is in circumferential contact with the cam surface and reciprocates in the radial direction when the two rotating members rotate relative to each other; and a plurality of fluids that change in volume as the cam body reciprocates. and a fluid passage formed in the second rotating member and communicating between the respective fluid chambers via an orifice, and due to the fluid resistance of the fluid flowing through the fluid passage due to the relative rotation of the two shafts, the distance between the two shafts is In the torque transmitting device in which the transmitted torque is controlled, the orifice is characterized in that the orifice area is controlled in accordance with the absolute rotational speed of the second rotating member.

Description

[Detailed explanation of the idea]

0001

[Industrial application field]

This idea is applicable to the driving force distribution device of 4-wheel drive vehicles, differential device between left and right wheels, or the difference between them. The present invention relates to a torque transmission device used as a differential limiting device that limits motion.

0002

[Conventional technology]

As a conventional torque transmission device of this kind, for example, Japanese Patent Application Laid-Open No. 62-286838, Japanese Patent Application Publication No. 63-285334 is known.

0003 For example, Japanese Patent Application Laid-open No. 62-286838 discloses a drive housing formed on the input shaft. The inner periphery of the drive housing is formed into a cam surface, and the driven housing formed on the output shaft is formed into a cam surface. The piston is inserted into the surface and inserted into the multiple cylinder holes recessed in the driven housing. The cam body is interposed between the cam surface and the back of the piston to form a fluid chamber. The outer circumferential side of the body is in contact with the cam surface, and each fluid chamber is communicated with a fluid path via an orifice. This is what I did.

0004 When the cam body rolls into contact with the cam surface due to the relative circuit between the input shaft and output shaft, the piston moves. As it moves, the volume of the fluid chamber changes and fluid pressure is generated in the fluid path, and this rotation between the two axes A structure in which torque is transmitted from the input shaft to the output shaft using fluid pressure proportional to the speed difference. It is constructed.

[0005] However, in such conventional devices, the value of the fluid pressure generated in the fluid path is is uniquely determined by the magnitude of the rotational speed difference between the input shaft and the output shaft, so the transmission As for the torque value, only one type of characteristic can be obtained depending on this rotational speed difference.

[0006] Therefore, for example, the transmission torque should be high enough at high speeds, and the transmission torque at low speeds. If you want to change the transmitted torque depending on the rotational speed of the input/output shaft, such as when you want to lower the Conventional devices cannot respond to such requests.

[0007]

[Problem that the idea aims to solve]

This idea allows torque to be transmitted between the input and output shafts depending on the relative rotational speed between the two shafts. At the same time, the torque transmission value changes depending on the magnitude of the absolute rotational speed of these two axes. The objective is to obtain the characteristics of

[0008]

[Means to solve the problem]

In order to solve the above-mentioned problem, this invention has a structure formed on one side of the relatively rotatable input/output shaft. a first rotary member having a cam surface on its inner peripheral portion; a second rotating member inserted into the cam surface; a second rotating member supported by the second rotating member; A cam body that circumferentially contacts the cam surface and reciprocates in the radial direction when the two rotating members rotate relative to each other; A plurality of fluid chambers whose volume changes as the body moves back and forth, and a second rotating member are formed. and a fluid path communicating between each fluid chamber via an orifice, and the relative rotation of the two shafts. The torque transmitted between the two shafts is controlled by the resistance of the fluid flowing through the fluid path. In a torque transmission device, The orifice changes its orifice depending on the absolute rotational speed of the second rotating member. It is configured so that the area is controlled.

[0009]

[Effect]

When relative rotation occurs between the first rotating member and the second rotating member, the cam surface is in contact with the cam surface. The cam body reciprocates in the radial direction according to the shape of the cam surface, and as the cam body reciprocates, the body In the fluid chamber where the volume changes, fluid pressure is generated due to flow resistance due to the orifice, and the cam body is pressed against the cam surface by this fluid pressure, which reduces the relative rotational speed difference between the two rotating members. Torque according to the amount is transmitted.

0010 And the orifice is provided with, for example, the absolute rotation of the second rotating member. The orifice area is controlled according to the speed, so the Fluid pressure is generated within the fluid chamber by the orifice.

[0011] Therefore, the transmitted torque increases in accordance with the relative rotational speed difference between the two rotating members, and , various transmission torques including transmission torque corresponding to the rotational speed of the second rotating member. characteristics can be obtained.

0012

【Example】

Examples of this invention will be described below with reference to the drawings.

[0013] FIG. 1 is a longitudinal sectional view of the torque transmission device 1 of this invention, and FIG. Line sectional view, FIG. 6 is an engine drive system of a four-wheel drive vehicle using the torque transmission device 1 of FIG. FIG.

[0014] The drive system in Figure 6 includes an engine 3, a transmission 5, and a front wheel drive system. It is equipped with a differential device 7, front wheel axles 9, 11, and front wheels 13, 15, and serves as a rear wheel drive system. Transfer gear train 17 and its drive pinion shaft (input shaft) 19, power Transmission device 1 and its output shaft 21, rear propeller shaft 23, rear wheel differential device 25, It includes rear wheel axles 27, 29 and rear wheels 31, 33.

[0015] The torque transmission device 1 illustrated in FIG. 1 includes a driven housing formed on an output shaft 21. (first rotating member) 35, first cam surface (cam surface) 37, second cam surface (cam surface) 39, the drive housing (second rotating member) 41 formed on the input shaft 19 and the first Oil chamber (fluid chamber) 43, second oil chamber (fluid chamber) 45, oil passage (fluid passage) 47, first ori Orifice 49, 2nd orifice 51, 1st drive driving ball (cam body) 53, second driving ball (cam body) 55, first piston The main components are a ton 57 and a second piston 59.

[0016] The inner periphery of the driven housing 35 has a groove whose major axis (or minor axis) is perpendicular to each other. A first cam surface 37 and a second cam surface 39 are formed in a circular shape, and the driven housing A housing cover 61 is screwed to the open end of the housing 35 .

[0017] The drive housing 41 is inserted into the cam surfaces 37 and 39 of the driven housing 35. The four first cylinder holes 63 and the second cylinder are arranged in the inserted state and are spaced at equal intervals in the radial direction. A cylinder hole 65 is formed, and a first piston 57 and a cylinder hole 65 are formed in these cylinder holes 63 and 65. The second piston 59 is tightly fitted, and the first cam surface 37 and the back of the first piston 57 are tightly fitted. A first driving ball 53 is placed between the second cam surface 39 and the back of the second piston 59. A second driving ball 55 is interposed between the two parts.

[0018] The first driving ball 53 and the second driving ball 55 are arranged in the circumferential direction. The drive housing 41 circumferentially contacts each of the cam surfaces 37 and 39 at a position shifted by 45 degrees. When the housing 35 and the driven housing 35 rotate relative to each other, the body moves back and forth, and the body A first oil chamber 43 and a second oil chamber 45 whose volume changes are connected to the cylinder holes 63, 65 and the piston. It is formed by tons 57 and 59.

[0019] The oil passage 47 is provided between the oil chambers 43 and 45 in correspondence with each cylinder hole 63 and 65. They are communicated via orifices 49 and 51.

[0020] The oil passage 47 is a radial oil passage 67, 6 provided at the bottom of each cylinder hole 63, 65. 9 and an axial oil passage 71.

[0021] The volume of the oil chambers 43 and 45 filled with oil is the same as that of the drive housing 41 and the drive housing. Although each volume changes due to relative rotation with the housing 35, the total volume The shapes of the cam surfaces 37 and 39 are set so that the cam surfaces 37 and 39 are constant.

[0022] The orifices 49 and 51 are provided in the drive housing 41 and The diameter of the drive housing 41 is configured to have a value corresponding to the absolute rotational speed of the drive housing 41. has been completed.

[0023] These orifices 49, 51 are shown in a representative enlarged view of the orifice 49 in FIG. As shown in the figure, it is arranged in a chamber 73 provided between the oil chamber 43 and the radial oil passage 47. a hollow box-shaped cylindrical body 75; and a small hole 77 that is inserted into and passes through the inner hole 76 of the cylindrical body 75. and a disc spring 81 interposed between adjacent plates 79, 79. , a communication hole 83 that communicates the inner hole 76 with the oil chamber 43, and a communication hole 83 that communicates the inner hole 76 with the oil chamber 43; and a communication hole 85 that communicates with the.

[0024] In the adjacent plates 79, 79, the small holes 77, 77 should not be brought close to each other. A gap is maintained between the disc springs 81 which are arranged in a staggered manner and are interposed. As a result, the oil flowing out from the first small hole 77 flows as shown by the arrow in Fig. 3. It is configured to flow through the gap S into the next small hole 77.

[0025] Therefore, the orifice area of the orifice 49 is determined by the size of this gap S. Therefore, when rotating together with the drive housing 41, these plates 79 Since the disc spring 81 is compressed and deformed by the centrifugal force acting on the disc spring 81, the gap S becomes smaller according to the magnitude of this centrifugal force, and the orifice area also becomes smaller. The resistance of oil passing through the fissure 49 increases. Also, the drive housing When the relative rotational speed difference △N between the ring 41 and the driven housing 35 increases, the original The plate 79 is pressed by the pressure generated in the orifices 49 and 51, and the surface of the orifice is Reduce the product.

[0026] Next, the operation of this embodiment will be explained.

[0027] When running at a constant speed with little resistance, the rotational speed difference between the input shaft 19 and the output shaft 21 is △ Since no N is generated, the drive housing 41 and driven housing 35 are compatible with each other. Since there is no counter-rotation and both driving balls 53 and 55 do not reciprocate in the radial direction, No transmission torque T is generated from the input shaft 19 to the output shaft 21.

[0028] When the accelerator pedal is suddenly depressed and the driver suddenly starts or accelerates, the When the front wheels 13 and 15 slip and a rotational speed difference △N occurs between the front and rear wheels, In this case, relative rotation occurs between the drive housing 41 and the driven housing 35, Due to this relative rotation, both driving balls 53, which are in contact with both cam surfaces 37, 39, 55 reciprocates in the radial direction, and during this reciprocating movement, each oil When the volumes of chambers 43, 45 are reduced, the flow through each orifice 49, 51 The pressure inside the oil chambers 43 and 45 increases due to the resistance, and this pressure is applied to the pistons 57 and 59. This acts to press the driving balls 53, 55 against the cam surfaces 37, 39.

[0029] This pressing force causes the transmission torque T to be transmitted from the input shaft 19 to the output shaft 21. Ru.

[0030] The value of this transmitted torque T is proportional to the rotational speed difference △N between the input shaft 19 and the output shaft 21. In addition, it is also proportional to the rotational speed of the input shaft 19 where the orifices 49 and 51 are provided. ing.

[0031] That is, while the rotational speed of the input shaft 19 is low, the orifices 49 and 51 are Since the centrifugal force acting on the plate 79 and the disc spring 81 is also small, the disc spring 81 The amount of deformation is also small, and the gap S between the plates 79 and 79 is large, and the flow The fluid pressure of the oil is low.

[0032] Therefore, the flow resistance due to the orifices 49 and 51 in this state is small, and the Since the pressing force of the contact balls 53 and 55 is also small, the transmitted torque T also remains small. , changes as shown by the dotted line in FIG.

[0033] On the other hand, when the input shaft 19 becomes high-speed, the centrifugal force acting on the plate 79 and the disc spring 81 Since the force increases in proportion to the square of the speed of the input shaft 19, as shown in FIG. The amount of deformation increases, the gap S becomes smaller, and the fluid pressure generated by this gap S becomes It gets expensive.

[0034] Therefore, the flow resistance of the orifices 49 and 51 at this time becomes large in a quadratic curve. As a result, the pressing force by the driving balls 53 and 55 becomes extremely large, and the transmitted torque increases. T changes as shown by the solid line in FIG.

[0035] In this way, even if the rotational speed difference △N is the same, the absolute rotational speed of the input shaft 19 is A transmission torque characteristic approximately proportional to the square of the meter value can be obtained. Became.

[0036] Such transmission torque characteristics are determined by the plate 7 constituting the orifices 49 and 51. 9 and the structure of the disc spring 81, especially the thickness of the plate 79 and the elasticity of the disc spring 81, etc. This can be easily changed by changing the settings.

[0037] In the illustrated example, the drive housing 4 has orifices 49 and 51 formed therein. 1 to the input shaft 19, that is, the transfer gear train 17 in the transmission diagram of FIG. However, if this is reversed, the output shaft 21 (driven shaft 35) may be coupled to the transfer gear train 17.

[0038] In the case of this reverse connection, for example, the wheel directly connected to the engine may slip during a sudden start. When the rotation speed of the output shaft does not suddenly increase, the orifice provided on the output shaft is The flow resistance at the systems 49 and 51 also does not increase suddenly, and therefore the flow resistance is not transmitted to the output shaft in this case. The torque that is reached has a gradual rise, allowing for a smooth start. .

[0039] The cam body is a cam body in which a driving ball and a piston are integrally formed. The number of orifices may also be one for each pair of cam bodies.

[0040] The number of fluid chambers provided in the drive housing 41, the shape of the cam surface, etc. Various numbers and shapes not shown can be used without any problem.

[0041]

[Effect of the idea]

As described above, according to this invention, the relative rotation difference between the first rotating member and the second rotating member The transmission torque of the corresponding value is transmitted, and the orifice is provided with this. The orifice area is controlled according to the absolute rotational speed of the rotating member, and this absolute rotation It generates fluid pressure according to the rotation speed, and the value of the transmitted torque changes depending on this fluid pressure. Ru.

[0042] Therefore, the transmission torque, which is determined according to the relative rotational speed difference between the two rotating members, has an original A transmission torque corresponding to the absolute rotational speed of the rotating member where the filter is installed is added. A torque transmission device that provides various transmission torque characteristics and is suitable for various usage situations. It became.

[Brief explanation of drawings]

FIG. 1 is a sectional view of an embodiment of this invention.

FIG. 2 is a sectional view taken along the line II-II in FIG. 1;

FIG. 3 is a cross-sectional view of the orifice used in the example.

FIG. 4 is a cross-sectional view showing a state where the rotational speed of the orifice in FIG. 4 is increased;

FIG. 5 is a transmission torque characteristic diagram of the embodiment.

FIG. 6 is an explanatory diagram showing a drive system of a four-wheel drive vehicle to which the embodiment is applied.

[Explanation of symbols]

19 Drive pinion shaft (input shaft) 21 Output shaft 35 Driven housing (first rotating member) 37 First cam surface (cam surface) 39 Second cam surface (cam surface) 41 Drive housing (second rotating member) 43 First oil chamber (fluid chamber) 45 Second oil chamber (fluid chamber) 47 Oil path (fluid path) 49 First orifice (orifice) 51 Second orifice (orifice) 53 1st driving ball (cam body) 55 Second driving ball (cam body)

Claims (1)

[Scope of utility model registration request] Claims: 1. A first rotary member formed on one of relatively rotatable input/output shafts and having a cam surface on the inner circumference; and a first rotating member formed on the other input/output shaft and inserted into the cam surface. two rotating members; a cam body that is supported by the second rotating member and is in circumferential contact with the cam surface and reciprocates in the radial direction when the two rotating members rotate relative to each other; and a plurality of cam bodies whose volume changes as the cam body reciprocates. and a fluid passage formed in the second rotating member and communicating between the respective fluid chambers via an orifice. 1. A torque transmission device in which transmission torque between shafts is controlled, wherein the orifice is configured such that its orifice area is controlled according to the absolute rotational speed of the second rotating member.