• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    pulley structure a pulley structure is proposed that can eliminate the application of an excessive force to a coil spring in order to prevent the coil spring itself from breaking and which can allow a project with a greater degree of freedom by freely changing the torque of friction, while restricting the ability to vary the friction torque. a drive pulley structure 1 has a cylindrical pulley element 2 around which a transmission belt 106 extends, a hub structure 3 which is provided within the pulley element 2 so as to rotate with respect to the element pulley 2, a helical spring 4 which is attached to the hub structure 3 at its end 4a, a recessed part 5 to which the other end 4b of the helical spring 4 is attached and which has a conical rounded surface as if it were part of a cone whose axis is constituted by the axis of rotation j of the cube structure 3, and a frictional element 6 which is inserted so as to be interposed between the conical rounded surface of the used part 5 and the pulley element 2, and the helical spring 4 is inserted to be interposed in place while being compressed in the direction of the rotation axis j of the cube structure 3, the grooved part 5, the frictional element 6 and the pulley element 2 being brought into contact with each other. are connected to each other by means of restoration p of helical spring 4.
    公开号:BR112013004876B1
    申请号:R112013004876-0
    申请日:2011-08-30
    公开日:2020-09-29
    发明作者:Tomokazu Ishida
    申请人:Mitsuboshi Belting Ltd；
    IPC主号:
    专利说明:

    TECHNICAL FIELD
    The present invention relates to a pulley structure having a pulley element and a hub structure that can rotate with respect to the pulley element. FUNDAMENTALS
    In general, as a transmission mechanism for transmitting power from an engine in a motor vehicle, there is a belt transmission mechanism in which a belt forms a loop between pulleys. In addition, as a pulley structure that is used in such a belt drive mechanism, a pulley structure is known to have a configuration to mitigate a change in rotation when the change in rotation is generated in one of the two rotating elements (see , for example, Patent Document 1).
    As a technique of this type, Patent Document 1 describes a pulley that includes an annular pulley element, a hub structure (to which the shaft of an alternating current generator is attached so as not to rotate to it), and a helical spring which is mounted between the ring pulley element and the hub structure. According to this configuration, when a change in rotation is generated in the hub structure, the helical spring between the hub structure and the ring element of the pulley is elastically deformed, thus attenuating the change in rotation.
    However, when the natural frequency of the pulley described in Patent Document 1 above is set to be equal to or less than a frequency that is considered from experience to be generated by an engine speed of revolution when an engine is idle, a situation in which the pulley resonates when the motor starts the rotation or stops the rotation. As a result, the relative displacement of distortion between the annular element of the pulley and the hub structure is increased sharply, and an excessive force is applied to the helical spring leading to another problem, as the failure of the helical spring itself is produced.
    To face this problem, a pulley structure has been proposed that adopts a spring clutch construction. As discussed in Patent Document 2, for example, in this pulley structure an extreme portion of a helical spring is not directly attached to a pulley element or to a hub structure. The extreme portion of the coil spring is elastically deformed in a radial direction, and is then fixed to the pulley element or the hub structure by means of a coil spring restoring force. Then, when an input torque that exceeds the frictional torque that is generated between the helical spring end portion and the pulley element or the hub structure is applied to the pulley element or hub structure, a slipping between the extreme portion of the coil spring and the pulley element or the hub structure, to eliminate the application of excessive force to the coil spring, thus avoiding the break of the coil spring itself. RELATED TECHNICAL DOCUMENT PATENT DOCUMENTS Patent Document 1: Japanese Patent No. 3268007 Patent Document 2: JP-A-2003-322174 SUMMARY OF THE INVENTION PROBLEMS THAT THE INVENTION MUST SOLVE
    When a spring clutch construction like the one described above is adopted, as the helical spring is produced using a plastic deformation technique, it is difficult to obtain uniform dimensions and profile accuracy, causing a problem, since the frictional torque generated between the extreme portion of the coil spring and the pulley element or hub structure tends to vary easily. In addition, the frictional torque generated between the extreme portion of the coil spring and the pulley element or hub structure is determined by the material and performance of the coil spring and the pulley element or hub structure. However, the selection of material and performance for a coil spring to be used is limited (the degree of freedom in the design is reduced) from the point of view of guaranteeing the elastic force of the coil spring and ensuring the force of the pulley element / hub structure, resulting in a case in which the friction torque required by the user cannot be implemented.
    Consequently, the invention was made aiming to solve the problems described above, and one of its objectives is to propose a pulley structure that can prevent the application of an excessive force on a helical spring, thus preventing the helical spring from breaking properly. and it can also increase the degree of freedom in the project by freely changing the friction torque while restricting the ability to vary the friction torque. MEANS FOR SOLVING PROBLEMS
    According to a first aspect of the invention, a pulley structure including a cylindrical pulley element around which a belt is extended is proposed, a hub structure that is provided within the pulley element, in order to rotate in relation to to the pulley element, a helical spring that is attached to the hub structure or to the pulley element at one of its ends, a slotted part to which the other end of the helical spring is attached and which has a rounded conical surface as if it were part of a cone whose axis was constituted by an axis of rotation of the cube structure, and a frictional element that is inserted to be interposed between the rounded conical surface of the stretched part and the pulley element, or between the conical rounded surface of the part and the cube structure, the coil spring being inserted so that it is interposed in its position, while being compressed in the direction of the axis of rotation of the cu structure bo, and the stretched part, the frictional element and the pulley element are placed in contact with compression with each other, or else the stroked part, the frictional element and the hub structure are placed in contact with compression with each other by the effect of a helical spring restoring force.
    According to the configuration described above, the blown part is compressed for contact by the effect of the restoring force of the helical spring, and the conical rounded surface of the blown part which is thus compressed for contact is then brought into contact with compression with the pulley or the cube structure by means of the frictional element. Adopting this configuration, a frictional torque is generated between the rounded conical surface of the stroked part and the frictional element. Consequently, when an input torque that is greater than the frictional torque is introduced from the pulley element or the hub structure, a relative slip can be generated between the conical rounded surface of the stretched part and the frictional element on a surface of compression contact between them, in order to prevent the helical spring from being distorted to a certain level or above it. By preventing the distortion of the coil spring to a certain level or above it in the manner described above, the durability of the coil spring can be increased. In addition, the frictional element and the blunt part that has a rounded conical surface can be produced with good precision by cutting or molding using a mold, and therefore the frictional torque may have its variation restricted. In addition, by freely changing the material / performance of the friction element, the desired friction torque can be adjusted, making it possible to increase the degree of freedom in the design.
    Furthermore, according to a second aspect of the invention, a pulley structure is provided as shown in the first aspect of the invention with the frictional element being fixed to the pulley element or to the hub structure, so that the frictional element is allowed to slide in relation to the stretched part only.
    According to the configuration described above, by attaching the frictional element to the pulley element or to the hub structure, the frictional element is allowed to slide in relation to the stretched part only. By adopting this configuration, a value can be determined for the frictional torque that is generated between the conical rounded surface of the stroked part and the frictional element only taking into account the value of the static friction coefficient between the frictional element and the stretched part.
    In addition, according to a third aspect of the invention, a pulley structure as proposed in the first or second aspect of the invention is proposed, in which as a form of fixing the helical spring, a form is adopted in which at least one of one end and the other end of the coil spring is locked on at least one of the hub structure, the pulley element and the flared part due to the restoring force of the coil spring while being elastically deformed in a radial direction, and a slip is generated when a rotation torque that is greater than the frictional torque that is generated between at least one end and the other end of the coil spring and at least one of the hub structure, the pulley element and the stretched part is applied.
    According to the configuration described above, it is possible to generate the frictional torque that is generated between the conical rounded surface of the affected part and the frictional element and the frictional torque that is generated between at least one of the one end and the other end of the coil spring and at least one of the hub structure, the pulley element, and the recessed part. Adopting this configuration, the value of the frictional torque that is generated between the helical spring and at least one of the hub structure, the pulley element and the stretched part and the value of the frictional torque that is generated between the rounded surface tapered portion and the frictional element can be freely changed to increase the degree of freedom in the design.
    In addition, according to a fourth aspect of the invention, a pulley structure as proposed in the third aspect of the invention is proposed, in which the frictional torque that is generated between the rounded tapered surface of the stretched part and the frictional element and the torque of friction that is generated between the coil spring and at least one of the hub structure, the pulley element and the stretched part have different values.
    According to the configuration described above, causing the frictional torque that is generated between the conical rounded surface of the stroked part and the frictional element and the frictional torque that is generated between the helical spring and at least one of the structure of the hub, of the pulley element, and of the stretched part have different values, it is possible to determine, based on the magnitude of the rotation torque that is applied to the pulley element or the cube structure, the place where the slip occurs, ie , or between the conical rounded surface of the stretched part and the frictional element or between the helical spring and at least one of the hub structure, the pulley element and the stretched part. ADVANTAGE EFFECTS OF THE INVENTION
    It is possible to propose the pulley structure that can inhibit the application of an excessive force on the helical spring to prevent the helical spring from breaking properly and that can increase the degree of freedom in the design by free alteration of the friction torque, restricting to the the possibility of varying the friction torque. BRIEF DESCRIPTION OF THE DRAWINGS
    Figure 1 is a schematic block diagram of a first mode auxiliary drive belt system.
    Figure 2 is a plan view of a drive pulley structure according to the first embodiment.
    Figure 3 is a sectional view taken along line A-A containing an axis of rotation of the drive pulley structure shown in Figure 2.
    Figure 4 is a diagram showing in detail the drive pulley structure shown in Figure 3.
    Figure 5 is a plan view of a drive pulley structure according to a second embodiment.
    Figure 6 is a sectional view taken along line B-B that contains an axis and rotation of the drive pulley structure shown in Figure 5.
    Figure 7 is a diagram showing in detail the drive pulley structure shown in Figure 6.
    Figure 8 is a sectional view containing an axis of rotation of a drive pulley structure according to a third embodiment. WAYS TO IMPLEMENT THE INVENTION First Mode
    A first embodiment of the invention will now be described. As shown in Figure 1, this modality describes an example where the invention is applied to a drive pulley structure 1 that is used in an auxiliary drive belt system 100 that drives an auxiliary (a water pump or alternator) by torque of an output shaft 101 of a motor vehicle engine. Note that the drive pulley structure 1 is used to eliminate a variation in tension of a drive belt 106 that is attributed to a change in engine speed. Auxiliary Drive Belt System 100
    Figure 1 is a schematic block diagram of the auxiliary drive belt system 100 of this modality. As shown in Figure 1, the auxiliary drive belt system 100 has the drive pulley structure 1 (a pulley structure) that is connected to the motor output shaft 101 (an alternate engine crankshaft or an eccentric drive shaft). a rotary motor), driven shafts (auxiliary shafts) 102, 103 that are connected to auxiliaries such as a water pump and alternator, a driven pulley structure 104 that is mounted on driven shaft 102, a driven pulley structure 107 that the driven shaft 103 is mounted and the drive belt 106 forms a loop over the drive pulley structure 1, the driven pulley structure 104 and the driven pulley structure 107. In this embodiment, a V-ribbed belt having a multiplicity V-shaped ribs extending parallel to each other along a longitudinal direction of the belt is used as the drive belt 106.
    In the auxiliary drive belt system 100, when the drive pulley frame 1 is driven to rotate through the torque of the output shaft 101, the drive belt 106 is driven due to the rotation of the drive pulley frame 1. Consequently , the driven pulley structure 104 and the driven pulley structure 107 are driven to rotate while the drive belt 106 runs in a loop, resulting, although not shown, that auxiliaries such as the water pump and alternator are driven which are connected to driven axes 102, 103. Setting the Drive Pulley Structure 1
    Next, the drive pulley structure 1 that is driven to rotate according to the torque of the output shaft 101 will be described in detail. Figure 2 is a plan view of the drive pulley structure 11. In addition, Figure 3 is a sectional view taken along line AA containing a rotation axis j of the drive pulley structure 1 shown in Figure 2. In addition, Figure 4 is a diagram showing in detail the pulley structure of drive 1 shown in Figure 3.
    As shown in Figures 2 and 3, the drive pulley structure 1 has a cylindrical pulley element 2 around which the drive belt 106 is placed to extend, a hub structure 3 that is connected to the output shaft 101 and that a helical spring 4 is provided within the pulley element 2 which is attached to the hub structure 3 at one end 4a of it, a recessed part 5 to which the other end 4b of the helical spring 4 is attached and which has a outer circumferential surface 5a which has a conical rounded surface as if it were part of a cone whose axis is formed by the axis of rotation J of the cube structure 3, and a frictional element 6 which is inserted to be interposed between the outer circumferential surface 5a of tapered part 5 which has the rounded conical surface as if it were part of a cone and pulley element 2. Additionally, the pulley element 2 and the hub structure 3 are connected so as to rotate relative to each other p in the middle of a roller bearing 9. In addition, a sliding bearing 8 is provided so as to be interposed between the hub structure 3 and the recessed part 5.
    The pulley element 2 has a cylindrical shape, and a multiplicity of pulley grooves 2a are formed in an outer circumference of the pulley element 2 so as to extend in a circumferential direction of their own. Then the drive belt 106 is placed to extend around the outer circumference of the pulley element 2 in such a state that the multiplicity of v-shaped ribs that are provided for in the inner circumference of the drive belt 106 are engaged with the corresponding pulley grooves 2a.
    The cube structure 3 is also cylindrical in shape. The output shaft 101 is fitted within a cylindrical inner portion 3a of the hub structure 3 so as to traverse it. The output shaft 101 and the hub structure 3 are connected to each other by means of suitable connecting devices such as pins so as not to rotate with respect to each other. Additionally, as materials from which the pulley element 2 and the cube structure 3 are manufactured, for each of them we can mention a non-magnetic material (a paramagnetic material, a diamagnetic material or an anti-ferromagnetic material). More specifically as a non-magnetic material, we can mention, for example, an aluminum alloy, a titanium alloy or a synthetic resin. Note that the pulley element 2 and the hub structure 3 are connected together so as to rotate with respect to each other by rolling bearings 9.
    As shown in Figure 3, the grooved part 5 has a substantially U-shaped section. An inner circumferential surface of the grooved part 5 has a cylindrical shape and an outer circumferential surface its 5th has a conical rounded surface as part of a cone whose axis it consists of the axis of rotation J of the cube structure 3. In this case, as can be seen in Figure 4, observing in section, an angle θ that is formed by an extension 5L of the outer circumferential surface 5a that is formed on the surface conical rounded and the axis of rotation J is adjusted to be within the limits of 1 ° or more and less than 90 °. The sliding bearing 8 is interposed between the hub structure 3 and the housed part 5, and this allows the hub structure 3 and the housed part 5 to rotate with respect to each other.
    The frictional element 6 is inserted so as to be interposed between the outer circumferential surface 5a having the conical rounded surface and the pulley element 2, and the frictional element 6 itself is fixed to the pulley element 2 so as not to rotate. It is preferable that the friction element 6 is made of a material that has a superior wear resistance and resistance to deformation by compression. We can mention metals such as brass, coated with brass, bronze and coated with clad bronze and resins such as polyamide, polyacetal and polyarylate, for example. In addition, a coefficient of static friction between the blown part 5 and the friction element 6 is set to a value that allows a relative slip to be generated between the blown part 5 and the friction element 6 when a desired input torque is received. . More specifically, the static friction coefficient is adjusted based on the materials selected for the frictional element 6 and the grooved part 5, a mode of finishing / surface configuration (a configuration in which the recesses and projections are arranged, for example) of the frictional element 6 which is placed against the grooved part 5 or the angle θ formed by the extension 5L of the outer circumferential surface 5a and the axis of rotation J.
    An angled helical spring 4 is used for helical spring 4 in which an elongated linear element has a substantially rectangular cross-section, as shown in Figure 3, having a spiral shape. In addition, the coil spring 4 is attached to the hub structure 3 at one end 4a of its own and is attached to the grooved part 5 at the other end 4b in such a way that the coil spring 4 is compressed in the direction of the rotation axis J. Then , the blown part 5 and the frictional element 6 are brought into contact with compression with each other by a restoring force P of the helical spring 4 thereby compressed.
    More specifically, as shown in Figure 4, the blown part 5 is compressed to be counted by the restoring force P of the coil spring. Then the outer circumferential surface 5a which has the conical rounded surface of the blown part which is thus compressed for contact is brought into contact with compression with the frictional element 6 in order to compress it by the vertical drag N which is expressed by the following expression (1) in relation to the angle θ that is formed by the extension 5L of the external circumferential surface 5a and by the axis of rotation J, observed in section. N = P / sineθ ... (1)
    In addition, a frictional torque Tf that is generated between the outer circumferential surface 5a of the blown part 5 and the frictional element 6 when the outer circumferential surface 5a of the blown part 5 is brought into contact with compression with the frictional element 6 in order to compress it by vertical drag N expression by expression (1) above is expressed by expression (2) below: Tf = pxNxr = px P / sine θ x r ... (2) where: p: coefficient of static friction between the grooved part 5 and the frictional element 6. r: Average radius of the outer circumferential surface 5a having the rounded conical surface. Drive Pulley Structure Function 1
    Next, the function of the drive pulley structure 1 of this modality will be described. In this case, the function of the drive pulley structure 1 will be described based on the assumption that the output shaft 101 rotates when the motor is started to turn, with the torque being introduced in the drive pulley structure 1 of a its side of the cube structure 3 by means of the output shaft 101. Assuming that the torsional torque that is applied on the side of the cube structure 3 by means of the output shaft 101 is an inlet torque T (a variable), when the relationship between T and Tf is approximately a relationship expressed by expression (3) below, there is no slipping on a contact surface between the outer circumferential surface 5a of the stretched part 5 and the frictional element 6, and the spring helical 4 over a distortion in a circumferential direction to thus absorb the torsional torque T introduced. T <Tf ... (3) On the other hand, the relationship between R and Tf is approximately a relationship expressed by expression (4) below, the helical spring 4 does not suffer distortion in the circumferential direction, and there is a slip on the contact surface between the outer circumferential surface 5a of the blown part 5 and the frictional element 6, the torsional torque T being thus absorbed by the slip. T> Tf ... (4).
    According to the configuration described above, the blown part 5 is compressed to contact the restoring force P of the helical spring 4 and the outer circumferential surface 5a having the conical rounded surface of the blown part 5 which is thus compressed for contact is brought into contact with compression with the pulley element 2 by means of the frictional element 6 to compress it. In doing so, the frictional torque Tf is generated between the outer circumferential surface 5a having the conical rounded surface of the used part 5 and the frictional element 6. Then, when the input torque T which is greater than the frictional torque Tf is introduced from the cube structure 3, a relative slip occurs on the surface where the outer circumferential surface 5a with the conical rounded surface of the used part 5 and the frictional element 6 are compressed to contact each other, so that it can be prevented that the coil spring 4 is distorted to a certain level or above it. In this way preventing the helical spring 4 from being distorted to a certain level or above, the durability of the helical spring 4 can be increased. In addition, the friction element 6 and the tapered part 5 that has the conical rounded surface it generates the friction torque Tf can be produced with good precision by cutting or molding with a mold, and therefore the friction torque variation capacity Tf can be restricted. In addition, by freely changing the material / performance of the friction element 6, the desired friction torque Tf can be adjusted, thus making it possible to have a project with a greater degree of freedom.
    In addition, according to the configuration described above, by fixing the frictional element 6 to the pulley element 2 so that it does not rotate, the frictional element 6 is allowed to slip in relation to the thrust part 5 only. In this way, the value for the friction torque Tf that is generated between the outer circumferential surface 5a with the conical rounded surface of the outer wall 5 and the frictional element 6 can be determined taking into account only the value of coefficient of static friction between the frictional element 6 and the grooved part 5.
    In this embodiment, although the pulley structure according to the invention is applied to the drive pulley structure 1 which is connected to the freckle shaft 101 of the motor, the pulley structure according to the invention can be applied to driven pulley structures 104, 107 which are mounted on the driven axes (auxiliary axes) 102, 103 which are connected to the auxiliary ones such as the water pump and the alternator, respectively.
    When this occurs, in the auxiliary drive belt system 100, when the drive pulley structure 1 is driven to rotate by the torque of the output shaft 101, the drive belt 106 is driven by the rotation of the drive pulley structure 1. Then, as the drive belt 106 runs in a loop, the torque is introduced from one side of the pulley element 2 of the drive pulley structure 104 or drive pulley structure 107 to which the drive pulley is applied. pulley structure according to the invention. Assuming that the torsional torque introduced is an input torsional torque T (one variable), when the relationship between t and tf is approximately the relationship expressed by expression (3), there is no slip on the contact surface between the surface outer circumferential 5a of the grooved part 5 and the frictional element 6, but the helical spring 4 undergoes distortion in the circumferential direction so as to absorb the input torsional torque T. On the other hand, when the ratio between T and Tf is approximately equal to the ratio expressed by expression (4), the helical spring 4 does not suffer distortion in the circumferential direction, but a slip occurs on the contact surface between the outer circumferential surface 5a of the stroked part 5 and the frictional element 6 to thus absorb the input torque T. Second Mode
    Next, the drive pulley structure 201 according to a second embodiment will be described mainly with reference to different configurations of the first embodiment, omitting the description of configurations analogous to those of the first embodiment. Figure 5 is a plan view of the pulley structure 201. Additionally, Figure 6 is a sectional view taken along line BB that contains a axis of rotation J of the drive pulley structure 201 shown in Figure 5. In addition In addition, Figure 7 is a diagram showing in detail the drive pulley structure 201 shown in Figure 6. Configuring the Drive Pulley Structure 201
    As shown in Figures 5 and 6, the drive pulley structure 201 has a cylindrical pulley element 202 around which a transmission belt 106 extends, a hub structure 203 which is connected to an output shaft 101 and which a helical spring 204 is provided within the pulley element 202 which is attached to the pulley element 202 at one end 204b thereof, a recessed part 205 to which the other end 204a of helical spring 204 is attached and which has a circumferential surface inner 205a which has a conical rounded surface as if it were a part of a cone whose axis is constituted by the axis of rotation J of the hub structure 203, and a frictional element 206 which is inserted to be interposed between the inner circumferential surface 205a of the part tapered 205 that has the conical rounded surface as if it were of a cone and the cube structure 203. Additionally, the pulley element 202 and the cube structure 203 are connected by hand to rotate with respect to each other by means of a roller bearing 209 and a slide bearing 208.
    As shown in Figure 6, the hollow portion 205 has a substantially cylindrical shape. The inner circumferential surface 205a of the tapered part 205 has the rounded conical surface as if it were part of a cone whose axis constituted the axis of rotation J of the cube structure 203. Here, as shown in Figure 7, when seen in section, a angle θ which is formed by an extension 205L of the inner circumferential surface 205a which has a rounded conical surface and the axis of rotation J is adjusted to be between Io or more up to less than 90 °.
    The frictional element 206 is inserted to be interposed between the inner circumferential surface 205a having the tapered round surface and the cube structure 203, and the frictional element 206 itself is fixed to the cube structure 203 so as not to rotate.
    The coil spring 204 is attached to the pulley element 202 at one end 204b thereof and is attached to the bore part 205 at the other end 204a in such a state that the coil spring 204 is compressed in the direction of the rotation axis J. Then the grooved part 205 and the frictional element 206 are caused to compress in contact with each other by a restoring force P of the helical spring 204 thus compressed.
    More specifically, as shown in Figure 7, the blown portion 205 is compressed for contact by the restoring force P of the coil spring. Then the inner circumferential surface 205a which has the conical rounded surface of the blown part 205 which is thus compressed for contact and brought into contact with compression with the frictional element 206 in order to compress it by a vertical drag N which is expressed by the expression (1) described in the first modality in relation to the angle θ that is formed by the extension 205L of the internal circumferential surface 205a and by the axis of rotation J when observed in section.
    In addition, a frictional torque Tf that is generated between the inner circumferential surface 205a of the blown part 205 and the frictional element 206, when the inner circumferential surface 205a of the blown part 205 is brought into compression contact with the frictional element 206 so as to compressing it by the vertical drag N expressed by expression (1), is expressed by expression (2) which is described in the first modality. In the second embodiment, p is a coefficient of static friction between the grooved part 205 and the frictional element 206 and r is an average radius of the inner circumferential surface 205a having the rounded conical surface. Function of the Drive Pulley Structure 201
    Next, the function of the drive pulley structure 201 of this modality will be described. Here, the function of the drive pulley structure 1 will be described based on an assumption that the output shaft 101 rotates when the motor is started to operate, with the torque being introduced in the drive pulley structure 201 of a cube structure side 203 of the through the output shaft 101. Assuming that the torsional torque that is introduced on the cube structure side through the output shaft 101 is the input torsional torque T (a variable ), when the relationship between T and Tf is approximately a relationship (T <Tf) expressed by expression (3) described above, there is no slip on a contact surface between the inner circumferential surface 205a of the set part 205 and the frictional element 206, but the helical spring 204 undergoes distortion in a circumferential direction so as to absorb the input torsional torque T. On the other hand, the relationship between T and Tf is approximately a relationship (T> Tf) expressed by the expression (4) des As described above, helical spring 204 does not suffer distortion in the circumferential direction, but a slip occurs on the contact surface between the inner circumferential surface 205a of the thrust part 205 and the frictional element 206, with the input torque T being absorbed by the slip.
    According to the configuration described above, the blown part 205 is compressed for contact by the restoring force P of the helical spring 204, and the inner circumferential surface 205a which has the conical rounded surface of the blown part 205 which is thus compressed. for contact, it is placed in contact with compression with the hub structure 203 by means of the friction element 206 to compress it. In doing so, the frictional torque Tf is generated between the inner circumferential surface 205a having the tapered rounded surface of the used part 205 and the frictional element 206. Then, when the input torque T which is greater than the torque of friction Tf is introduced from the cube structure 203, a relative slip is produced on the surface where the inner circumferential surface 205a which has the conical rounded surface of the set part 205 and the frictional element 206 are compressed together to come into contact, so that distortion of the coil spring 204 can be prevented up to a certain level or above. By preventing the distortion of the coil spring 204 to a certain level or above it, the durability of the coil spring 204 can be increased. Additionally, the friction element 206 and the tapered portion 205 which has the conical rounded surface that generates the frictional torque Tf can be produced with good precision by cutting or milling Mold molding, and therefore the friction torque variation capacity Tf can be restricted. In addition, by freely changing the material / performance of the friction element 206, a desired friction torque Tf can be adjusted, making it possible to have designs with a greater degree of freedom.
    In addition, according to the configuration described above, fixing the frictional element 206 to the hub structure 203 so that it does not rotate, the frictional element 206 is allowed to slip only in relation to the set part 205. Third modality
    Next, a driven pulley structure 301 (a pulley structure) will be described according to a third modality, mainly in relation to different configurations of the first modality, omitting the description of configurations similar to those of the first modality. As shown in Figure 8, the driven pulley structure 301 according to the third embodiment adopts a configuration in which a spring clutch construction is incorporated in a portion where the helical spring 4 of the driving pulley structure 1 is the same provided in the first modality. Additionally, the third embodiment will be described as the drive pulley structure 301 according to the present invention being mounted on the driven shaft 102 of the auxiliary drive belt system 100 shown in Figure 1 for use as a driven pulley structure. Figure 8 is a sectional view containing a rotation axis J of the driven pulley structure 301. 301 Driven Pulley Structure Configuration
    In the driven pulley structure 301 according to the third modality, the configuration adopted in the first embodiment is not adopted in which the helical spring 4 of the driving pulley structure 1 is fixed directly to the thrust part 5 at its other end 4b, but as shown in Figure 8, a construction being adopted in which the other end 304b of a coil spring 304 is elastically deformed in a direction radially outward 0, so that the coil spring 304 is locked to be mounted on a recessed part 305 by a restoring force F (in a radially inward direction) yours. On the other hand, an end 304a of helical spring 304 is attached to a hub structure 303. Function of Driven Pulley Structure 301
    Next, the function of the driven pulley structure 301 of this modality will be described. First, the function of the driven pulley structure 301 will be described based on a case in which an output shaft 101 rotates when the engine is started and the torque of torque is introduced into the driven pulley structure 301 through the structure drive pulley 1 and drive belt 106. This case is based on the assumption that a rotation torque of the pulley element 304 exceeds a rotation torque of the hub structure 3 03 of the driven pulley structure 301 when starting to the engine to rotate.
    As in the case of the first modality, it is assumed that the torque that is introduced in the drive pulley structure 301 on the side of the pulley element 302 is an input torque T (a variable) and that a friction torque generated between a surface outer circumferential 305a of the set part 305 and a frictional element 306 is Tf, when the relationship between T and Tf is approximately the relationship (T <Tf) expressed by expression (3), no slip is produced on the contact surface between the circumferential surface outer part 305a of the housed part 305 and the frictional element 306. Additionally, the helical spring 304 has the diameter contracted due to contact with the clutch surface 305c of the housed part 305.
    Then the helical spring 304 undergoes distortion in a circumferential direction and is held against the clutch surface 3 0 5c with an increase of the contact engagement force with pressure relative to the clutch surface 305c, with no slip occurring, the rotation of the element being pulley 302 transmitted to hub structure 303. Then, an auxiliary is activated such as a water pump or alternator that is connected to driven shaft 102 which is mounted on hub structure 303.
    On the other hand, when the relation between T and Tf is approximately the relation (T> Tf) expressed by expression (4), the helical spring 304 has its diameter contracted as a result of contact with the clutch surface 305c of the thrust part 305 and is held against the clutch surface 305c with the increased pressure contact engagement force relative to the clutch surface 305c, with no slip occurring. However, a slip occurs on the contact surface between the outer circumferential surface 305a of the blown-out part 305 and the frictional element 306 to thereby absorb the input torque T. Thus absorbing the input torque T, the rotation of the pulley element 3 02 is not transmitted to the hub structure 303, and the pulley element 302 can rotate freely.
    Next, the function of the driven pulley structure 3 01 will be described based on a case in which, although the rotation torque of the pulley element 302 is reduced by means of a belt transmission of 106 when the output shaft 101 stops from rotate as a result of the engine stopping, the rotation torque of the hub structure 303 exceeds the rotation torque of the pulley element 302 due to the inertia produced when the motor spins, that is, a case in which the torque is introduced into the drive structure pulley driven on one side of hub structure 303.
    Assuming that the torque that is introduced in the driven pulley structure 301 on the side of the hub structure 033 is an input torque T (a variable), that a frictional torque generated between the outer circumferential surface 305a of the set part 305 and the frictional element 306 is Tf and that a frictional torque generated between the helical spring 304 and the clutch surface 305c is Ts, when the relationship between the frictional torques is such that T <Ts <Tf, no slip will occur in the contact surface between the outer circumferential surface 305a of the blown-out part 305 and the frictional element 306. Additionally, the helical spring 304 is held against the clutch surface 305c and no slip occurs, the rotation of the hub structure 303 being transmitted to the element pulley 302.
    In addition, when the relationship between the frictional torques is such that Ts <T <Tf, no slipping will occur on the contact surface between the outer circumferential surface 305a of the blown-out part 305 and the frictional element 306. On the other hand, the helical spring 304 has the expanded diameter and the contact pressure force relative to the clutch surface 305c is weakened, which causes a slip to occur in a contact portion between the helical spring 304 and the clutch surface 305c. Thus, the rotation of the hub structure 303 is not transmitted to the pulley element 302, thus freely rotating the hub structure 303.
    Furthermore, when the relationship between the frictional torques is such that Ts <Tf <T, the helical spring 304 will have the diameter expanded, and the contact pressure force relative to the clutch surface 305c will be weakened, which does causing a slip to occur in the contact portion between the coil spring 304 and the clutch surface 305c. Thus, the rotation of the hub structure 303 is not transmitted to the pulley element 302, thus rotating the hub structure 303 freely.
    Here, in the third embodiment, the relationship between the frictional torque Tf that is generated between the outer circumferential surface 305a of the thrust part 305 and the frictional element 306, and the frictional torque Ts that is generated between the helical spring 304 and the surface clutch 305c is such that Ts <Tf. However, by freely adjusting the values of the friction torques Ts, Tf (by adjusting the values of Ts and Tf to different values), it is possible to determine, based on the magnitude of the input torque T, where to produce a slip that is, either between the outer circumferential surface 305a of the thrust portion 305 and the frictional element 306 or between the helical spring 304 and the clutch surface 305c.
    Describing, for example, a case in which the rotation torque of the hub structure 033 exceeds the rotation torque of the pulley element 32, due to the inertia produced when the motor rotates, that is, a case in which the torque is introduced into the drive pulley structure 301 on the side of the hub structure 303, the relationship between the frictional torques Tf, Ts being such that TfcTs, when the frictional torques are related to the input torque T in such a way , that Tf <T <Ts, the coil spring 304 is held against the surface of the clutch 305c, with no slipping occurring, whereas a slip is produced on the contact surface between the outer circumferential surface 305a of the set part 305 and the element rub 306, thus the rotation of the hub structure 303 is not transmitted to the pulley element 302 and the hub structure 303 rotates freely.
    In addition, when the frictional torques are related to the input torque T, in such a way that Tf <Ts <T, a slip occurs on the contact surface between the outer circumferential surface 305a of the set part 305 and the frictional element 306, the rotation of the hub structure 303 not being transmitted to the pulley element 302, and the hub structure 303 rotates freely.
    Note that the driven pulley structure 301 works in the same way also when the driven pulley structure 301 is mounted on the output shaft 101 for use as a drive pulley structure. In this case, the output shaft 101 rotates when the motor is started to turn, the torque is introduced into the driven pulley structure 301 on the side of the hub structure 303 through the output shaft 101, then exceeding the rotation torque of the hub structure 303 the rotation torque of the pulley element 302. On the other hand, when the output shaft 101 interrupts rotation due to engine interruption, the rotation torque of the pulley element 302 exceeds the rotation torque of the pulley structures hub 303 due to the fact that the drive belt 106 is driven by inertia, thus the torque is introduced in the driven pulley structure 301 on the side of the pulley element 302.
    In addition, the third embodiment adopts the construction in which the other end 304b of helical spring 304 is elastically deformed in the radially outward direction O, so that helical spring 304 is locked to be mounted on the thrust part 305 by its restoring force F (in the radially inward direction). However, the invention is not limited to such a construction. A construction can be adopted in which the other end 304b of helical spring 304 is elastically deformed in the direction radially inward, so that the helical spring 304 is locked to be mounted on the blown part 305 by a restoring force thereof ( in the radially outward direction).
    In addition, in the third embodiment, one end 304a of helical spring 304 is attached to hub structure 303. However, like the other end 304b of helical spring 304, one end 304a of helical spring 304 can be resiliently deformed in the radially outward direction instead of being attached to the hub structure 303, so that one end 304a of the helical spring 304 is locked on the hub structure 303 by a restoring force thereof (in the radially inward direction) .
    In addition to the driven pulley structure 301 according to the third embodiment, the configuration is adopted in which the spring clutch construction is incorporated in the portion in which the helical spring 4 of the driving pulley structure 1 is as proposed in the first embodiment. However, a configuration can be adopted in which the spring clutch construction is incorporated in the portion in which the helical spring 204 of the drive pulley structure 201 is provided as in the second embodiment. When this occurs, the other end 204a of the helical spring 204 is elastically deformed in the radially outward direction, so that the helical spring 204 is locked in the biased part 205 by a restoring force thereof (in the radially inward direction). Additionally, one end 204b of helical spring 204 can be attached to the pulley element 202 or it can be elastically deformed in the direction radially outward (inward), such as the other end 204a of helical spring 204, so that one end 204b of the helical spring 204 is locked in the pulley element 202 by a restoring force (in the direction radially inward [outward]).
    According to the configuration described above, it is possible to generate the two frictional torques which are the frictional torque Tf which is generated between the outer circumferential surface 305a which has a tapered round surface of the set part 305 and the frictional element 306 and the frictional torque Ts that is generated between the other end 304b of helical spring 304 and the clutch surface 305c of the thrust part 305. Generating the two frictional forces as described above, for example, when the driven pulley structure 301 of according to the invention it is mounted on the driven shaft 102 to be used as the driven pulley structure, with the input torque T inserted on the side of the pulley element 302, if the input torque T is greater than the friction torque Tf that is generated between the outer circumferential surface 305a of the set part 205 and the frictional element 306, the input torque T can be absorbed by producing a slip on the contact surface between the outer circumferential surface 305a of the blown-out part 305 and the frictional element 306. On the other hand, with the input torque T introduced from the hub structure 303 on the side, in the event that the respective friction torques are related to the input torque T, so that Ts <T <Tf, there is no slip on the contact surface between the outer circumferential surface 305a of the blown part 305 and the frictional element 306, but a slip is produced in the helical spring 304 in the contact portion between the helical spring 304 and the clutch surface 305c. Thus, the rotation of the hub structure 033 is not transmitted to the pulley element 302, thus allowing the hub structure 303 to rotate freely. In addition, if the respective frictional torques are related to the input torque T in such a way that Ts <Tf <T, a slip occurs in the coil spring 304 in the contact portion between the coil spring 304 and the clutch surface 305c, and the rotation of the hub structure 033 is not transmitted to the pulley element 302, thus allowing the hub structure 303 to rotate freely. By adopting this configuration, it is possible to have a design with a greater degree of freedom, freely changing the values of the friction torque Ts that is generated between the other end 03 04b of the helical spring 304 and the clutch surface 305c of the tapered part 305, and the frictional element Tf which is generated between the outer circumferential surface 305a having a tapered round surface of the tapered portion 305 and the frictional element 306.
    In addition, by freely adjusting the values of the frictional torques Ts, Tf (by adjusting the values of Ts and Tf to different values), it is possible to determine based on the magnitude of the input torque T where to produce a slip, this , or between the outer circumferential surface 305a of the thrust part 305 and the frictional element 306 or between the helical spring 304 and the clutch surface 305c.
    Thus, although modalities of the invention have been described above, the invention is not limited to the modalities described above, but can be implemented by introducing several changes without departing from the scope of the claims to be described below.
    Although the patent application has been described in detail and with reference to specific modalities, it is obvious to those skilled in the art to which the invention belongs that several changes and modifications can be made to it without deviating from the spirit and scope of the invention.
    This patent application is based on the Japanese Patent Application (No. 2010-193935) filed on August 31, 2010, the content of which is incorporated by reference into this document. DESCRIPTION OF REFERENCE NUMBERS

    权利要求:
    Claims (6)
    [0001]
    1. Pulley structure, characterized by the fact that it comprises: a cylindrical pulley element around which a belt extends; a cube structure which is provided within the pulley element so as to rotate with respect to the pulley element; a helical spring that is attached to the hub structure at its first end; a recessed part to which a second end of the coil spring is contacted and which has a rounded conical surface as if it were part of a cone whose axis is constituted by an axis of rotation of the cube structure; a frictional element which is inserted to be interposed between the rounded conical surface of the stroked part and the pulley element, and a clutch surface on an inner circumferential surface of the stroked part, the inner circumferential surface of the stroked part being substantially parallel to the axis of rotation of the cube structure, being that: the helical spring is inserted to be interposed in its place while being compressed in the direction of the axis of rotation of the cube structure; an axial restoring force of the helical spring impels the blown part, the frictional element and the pulley element in contact by compression with each other; the second end of the coil spring contacts the clutch surface; and the second end of the coil spring is elastically deformed in a radial direction to urge the second end of the coil spring towards the clutch surface due to a radial restoring force of the coil spring and the second end of the coil spring contacts the clutch surface with a pressure contact engagement force that varies based on a relationship between an introduced rotation torque and a first friction torque, and the first friction torque is generated between the second end of the coil spring and the surface of clutch.
    [0002]
    2. Pulley structure, according to claim 1, characterized by the fact that: the frictional element is fixed to the pulley element, so that the frictional element is allowed to slip only in relation to the stretched part.
    [0003]
    3. Pulley structure according to claim 1, characterized by the fact that the pulley structure is configured in such a way that: the helical spring is propelled to expand in diameter and causes a slip at a point of contact between the helical spring and the clutch surface when the introduced torque is greater than the first frictional torque that is generated between the second end of the coil spring and the clutch surface.
    [0004]
    4. Pulley structure, according to claim 3, characterized by the fact that the pulley structure is configured in such a way that: the conical rounded surface of the stroked part and the frictional element generate a second friction torque between them; the second end of the coil spring and the clutch surface generate the first frictional torque between them; and the first friction torque and the second friction torque have different values.
    [0005]
    5. Pulley structure, according to claim 1, characterized by the fact that the helical spring has a contracted diameter.
    [0006]
    6. Pulley structure according to claim 1, characterized by the fact that when the introduced rotation torque is less than the first frictional torque that is generated between the second end of the coil spring and the clamped surface of the stretched part , the coil spring is driven to contract in diameter and the pressure contact engagement force between the second end of the coil spring and the clutch surface is increased; and when the entered rotation torque is greater than the first frictional torque that is generated between the second end of the coil spring and the clamped part surface, the coil spring is driven to expand in diameter and the engagement force pressure contact between the second end of the coil spring and the clutch surface of the blown part is weakened.
    类似技术:
    公开号 | 公开日 | 专利标题
    BR112013004876B1|2020-09-29|PULLEY STRUCTURE
    US3396556A|1968-08-13|Flexible coupling
    BR112013012483A2|2020-08-04|insulating decoupler
    JP2006177548A|2006-07-06|Pulley for power transmission member, separate starter-alternator fitted with such pulley, and engine drive system
    KR20130108516A|2013-10-04|Isolation pulley with overrunning and vibration damping capabilities
    CN109312789A|2019-02-05|Belt pulley decoupler
    CN105452715A|2016-03-30|Harmonic gear device
    KR101834815B1|2018-03-06|Dual-type wave gear device
    KR101918011B1|2018-11-13|Dual-type wave gear device
    CN103925332A|2014-07-16|Self-regulation centrifugal rotating friction damper
    ES2286004T3|2007-12-01|MULTIDISCO CLUTCH WITH HELICOIDAL MEDIA TO DYNAMICALLY ADJUST THE AXIAL COMPRESSION LOAD ON THE DISCS.
    US20100258395A1|2010-10-14|Braking device, in particular for rolling curtains, shutters, mosquito nets and the like
    US2196716A|1940-04-09|Torque coupling
    JP6895319B2|2021-06-30|Tortional damper
    US1550779A|1925-08-25|Frictional slack-motion shaft coupling
    US1702057A|1929-02-12|Flexible shaft coupling
    JP2008202739A|2008-09-04|Pulley structure
    US1488740A|1924-04-01|Resilinet universal joint for power transmission
    US1440847A|1923-01-02|Flexible coupling
    EP3358219B1|2021-11-03|Sliding contact-type wave generator, strain wave gearing device, and wave-generating method
    US3199312A|1965-08-10|Torque coupling and safety clutch device
    US4385896A|1983-05-31|Split coupling
    US20100181878A1|2010-07-22|Power output device and power enhancement member
    US3918652A|1975-11-11|Core chucks
    US20210293285A1|2021-09-23|Torque limiting coupler for an electric motor shaft
    同族专利:
    公开号 | 公开日
    EP2626595A1|2013-08-14|
    BR112013004876A2|2016-05-03|
    EP2626595B1|2019-08-07|
    JP2012052576A|2012-03-15|
    JP5515084B2|2014-06-11|
    CN103080608A|2013-05-01|
    WO2012029815A1|2012-03-08|
    CA2808060C|2018-05-22|
    US9638308B2|2017-05-02|
    US20130150191A1|2013-06-13|
    CA2808060A1|2012-03-08|
    EP2626595A4|2014-02-26|
    CN103080608B|2016-01-20|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US5139463A|1991-06-05|1992-08-18|Litens Automotive Partnership|Serpentine drive with coil spring alternator connection|
    JP4013384B2|1999-02-05|2007-11-28|株式会社ジェイテクト|Pulley unit with one-way clutch|
    DE10012233A1|2000-03-14|2001-09-20|Schaeffler Waelzlager Ohg|Automotive pulley drive wheel with friction slip clutch and helical spring on a hub|
    JP2003322174A|2002-05-07|2003-11-14|Ntn Corp|Spring clutch|
    BRPI0417395B1|2003-12-09|2016-06-07|Litens Automotive Inc|decoupler assembly to transfer torque between a drive shaft and an endless drive element of an automotive engine|
    JP2006038183A|2004-07-30|2006-02-09|Koyo Seiko Co Ltd|Power transmission|
    JP5026687B2|2004-12-02|2012-09-12|三ツ星ベルト株式会社|Pulley structure|
    BRPI0606764B1|2005-02-03|2018-10-30|Litens Automotive Inc|decoupler assembly to transfer torque between a shaft and a drive belt|
    EP1754914A1|2005-08-19|2007-02-21|Industrias Cántabras de Torneado S.R.L.|Alternator pulley|
    JP4957264B2|2007-01-24|2012-06-20|株式会社ジェイテクト|Pulley unit|
    US8529387B2|2008-04-30|2013-09-10|Dayco Ip Holdings, Llc|Pulley with asymmetric torque-sensitive clutching|US8784244B2|2008-04-30|2014-07-22|Dayco Ip Holdings, Llc|Pulley with asymmetric torque-sensitive clutching|
    US8888622B2|2012-06-04|2014-11-18|The Gates Corporation|Isolator decoupler|
    CN102758860B|2012-07-27|2015-04-15|重庆大易用机械有限公司|Conical-surface friction type overrunning clutch|
    US11236812B2|2012-09-10|2022-02-01|Zen S/A Industria Metalurgica|Decoupler with one-way clutch and fail-safe system|
    BR102012022803B1|2012-09-10|2017-05-02|Zen S/A Indústria Metalúrgica|decoupler with freewheel system and vibration damping|
    KR101500138B1|2013-09-10|2015-03-06|현대자동차주식회사|Decoupling device of crank pully|
    WO2015048885A1|2013-10-01|2015-04-09|Litens Automotive Partnership|Decoupler with controlled damping|
    US9169914B2|2014-03-07|2015-10-27|Gates Corporation|Isolating decoupler|
    US9341254B2|2014-08-08|2016-05-17|Gates Corporation|Isolating pulley|
    US9759274B2|2014-08-18|2017-09-12|Gates Corporation|Accessory tuning device with spring lock|
    US9291253B1|2015-03-24|2016-03-22|Gates Corporation|Isolating decoupler|
    US9784357B2|2015-04-27|2017-10-10|Ningbo Yangtong Automobile Parts Co., Ltd.|Overrunning alternator damping pulley|
    KR101724471B1|2015-05-26|2017-04-18|현대자동차 주식회사|Alternator unit having vibration reducing damper|
    US9618099B2|2015-07-13|2017-04-11|Gates Corporation|Tensioner with secondary damping|
    CN105715757A|2016-04-12|2016-06-29|无锡凯能光伏设备有限公司|Adjustable rotary drive device with safety clutch|
    FR3053394B1|2016-06-30|2019-08-09|Hutchinson|DECOUPLING PULLEY WITH DEPARTURE CLUTCH|
    JP6950954B2|2017-12-22|2021-10-13|国立大学法人金沢大学|Liquid filling method, SIMM probe manufacturing method, SIMM probe and SIMM|
    法律状态:
    2018-12-26| B06F| Objections, documents and/or translations needed after an examination request according [chapter 6.6 patent gazette]|
    2019-05-14| B06T| Formal requirements before examination [chapter 6.20 patent gazette]|
    2020-05-05| B09A| Decision: intention to grant [chapter 9.1 patent gazette]|
    2020-09-29| B16A| Patent or certificate of addition of invention granted [chapter 16.1 patent gazette]|Free format text: PRAZO DE VALIDADE: 20 (VINTE) ANOS CONTADOS A PARTIR DE 30/08/2011, OBSERVADAS AS CONDICOES LEGAIS. |
    优先权:
    申请号 | 申请日 | 专利标题
    JP2010-193935|2010-08-31|
    JP2010193935A|JP5515084B2|2010-08-31|2010-08-31|Pulley structure|
    PCT/JP2011/069669|WO2012029815A1|2010-08-31|2011-08-30|Pulley structure|
    [返回顶部]