JP2009243584A - Variable damping force type damper for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To obtain a variable damping force type damper for a vehicle capable of shutting off an influence of damper oil and comprising a friction generating means of simple structure. <P>SOLUTION: This variable damping force type damper for the vehicle comprises a friction generating means 50 for generating a friction force between a cylinder 21 and a rod 24. The friction generating means 50 is constituted of: a shoe member 51 arranged freely to move in the radial direction of the cylinder 21; a magnetic attracted member 52 arranged freely to move in the axial direction of the cylinder 21; an electromagnetic coil 54 arranged in the attracted member 52 at an axial end surface of the cylinder 21 so as to attract the attracted member 52; and a plate spring 55 interposed between the shoe member 51 and the attracted member 52 so as to move the shoe member 51 in the radial direction of the cylinder 21 when the attracted member 52 is moved in the axial direction of the cylinder 21. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a damper having a variable damping force for a vehicle which is incorporated in a suspension for a vehicle using friction and can change a damping force of the damper.

2. Description of the Related Art As a damper for a vehicle, a variable damping force type damper has been put to practical use in which an orifice is formed in a piston and a damping force is generated by a resistance for flowing oil flowing through the orifice.
In general, the damping force variable damper of a practical vehicle changes the damping force by changing the flow rate of oil flowing through the orifice by changing the diameter of the orifice.

As such a damping force variable damper of a vehicle, one in which the damping force of the damper is changed using an electromagnet is known (for example, see Patent Document 1).
Japanese Patent Laid-Open No. 11-2276 (5th page, FIG. 1-2)

The technique of Patent Document 1 will be described.
FIGS. 14A and 14B are views for explaining the basic configuration of a conventional damping force variable damper, and FIG. 14B shows an enlargement of the portion b in FIG.
The conventional damping force variable damper 300 includes a cylindrical cylinder 301, a piston 302 slidably attached to the cylinder 301, a damper oil 304 that flows in the cylinder 301 through an orifice 303 of the piston 302, A rod 306 having one end attached to the piston 302 and the other end protruding outside the cylinder 301 via the rod guide 305, and two (upper and lower) friction generations attached to the rod 306 and housed in the cylinder 301 Means 308 and 309.

  The upper friction generating means 308 includes an electromagnet 311 attached to the rod 306, an annular plate 312 driven by the electromagnet 311, cam means 313 formed on the electromagnet 311 side, and a plurality of balls on the cam means 313. And a shoe member 316 composed of a plurality of segments 315 attached to the annular plate 312 so as to be movable in the radial direction. The electromagnet 311 is excited, and the annular plate 312 is drawn toward the electromagnet 311 side. When this occurs, the shoe member 316 is brought into contact with the inner surface of the cylinder 301 to generate a frictional force and change the damping force of the damper. The lower friction generating means 309 has the same configuration as the upper friction generating means 308.

However, in the variable damping force damper 300 of the vehicle, friction generating means 308 and 309 which are mechanisms for generating friction between the cylinder 301 and the rod 306 are mainly composed of the shoe member 316, the ball 314, and the cam means (cam surface) 313. Therefore, the number of parts is large and the structure is complicated. Also, the assembly of the friction generating means 308 and 309 requires man-hours.
In addition, in the damping force variable damper 300 of the vehicle, when the pressing force of the shoe member 316 increases, there is a structure and technical problem corresponding to self-locking due to the “wedge structure” using the cam means (cam surface) 313. .

  Further, the friction generating means 308, 309 of the variable damping force damper 300 of the vehicle is a ball-cam type friction generating means for generating a rod pressing force due to a boosting effect by the “wedge structure”. In order to avoid the self-locking, there are cases where restrictions are imposed on the design of the friction generating means 308 and 309.

  The present invention provides a vehicle damping force that has a simple structure, can be easily assembled, does not require self-locking as a means for generating a frictional force, and can improve design flexibility. It is an object to provide a variable damper.

  The invention according to claim 1 is a cylindrical cylinder, a piston that is slidably attached to the cylinder, divides the cylinder into two chambers, a rod that is attached to the piston and protrudes outward from the cylinder, and a cylinder A damper having a variable damping force for a vehicle, comprising a damper oil sealed inside and flowing in two chambers through an orifice of a piston, and a friction generating means for generating a frictional force between a cylinder and a rod. The friction generating means includes a shoe member disposed so as to be movable in the radial direction of the cylinder, a magnetically attracted member disposed so as to be movable in the axial direction of the cylinder, and an axial end surface of the attracted member And is interposed between the shoe member and the member to be sucked, and is shunted when the member to be sucked moves in the axial direction of the cylinder. Characterized in that comprising a plate spring for moving the member in the radial direction of the cylinder.

  The invention according to claim 2 is characterized in that the friction generating means is disposed on one end face of the cylinder and outside the cylinder.

  The invention according to claim 3 is characterized in that the friction generating means is arranged inside a cylinder from which the rod is extended.

  The invention according to claim 4 is characterized in that the friction generating means is arranged on the cylinder side and the shoe member presses the outer peripheral surface of the rod.

  The invention according to claim 5 is characterized in that the friction generating means is disposed on the rod side and the shoe member presses the inner surface of the cylinder.

In the invention according to claim 1, a cylindrical cylinder is provided in the damping force variable damper of the vehicle, and a piston that divides the cylinder into two chambers is slidably attached to the cylinder and protrudes outward from the cylinder. A rod is attached to the piston, damper oil flowing through the two chambers through the piston orifice is sealed in the cylinder, and friction generating means for generating a frictional force between the cylinder and the rod is provided.
The friction generating means is arranged such that the shoe member is movable in the radial direction of the cylinder, and the attracted member of the magnetic material is movable in the axial direction of the cylinder, and is attracted to the axial end surface of the cylinder of the attracted member. An electromagnetic coil that attracts the member is disposed, and a leaf spring that moves the shoe member in the radial direction of the cylinder when the attracted member moves in the axial direction of the cylinder is interposed between the shoe member and the attracted member. .
That is, a leaf spring that is interposed between the shoe member and the member to be sucked and moves the shoe member in the radial direction of the cylinder when the member to be sucked moves in the axial direction of the cylinder. Compared with the case where a member such as a cam or a ball is used for the purpose, the structure is simplified and the assemblability is improved. As a result, the structure of the variable damping force damper of the vehicle can be simplified.

  In the invention according to claim 2, since the friction generating means is disposed on one end face of the cylinder and outside the cylinder, it can be easily mounted on a damper having a conventional structure. As a result, generalization of the friction generating means can be promoted.

  In the invention which concerns on Claim 3, a friction generation means is arrange | positioned inside the cylinder from which a rod is extended. Thereby, the damping force variable damper of a vehicle can be comprised compactly.

  In the invention according to claim 4, since the friction generating means is arranged on the cylinder side and the shoe member presses the outer peripheral surface of the rod, the shoe member can be small, and the friction generating means can be downsized. Can do.

  In the invention according to claim 5, since the friction generating means is arranged on the rod side and the shoe member presses the inner surface of the cylinder, the contact area of the shoe member can be greatly increased. As a result, a large frictional force can be generated between the cylinder and the rod, and the performance of the variable damping force damper of the vehicle can be improved.

The best mode for carrying out the present invention will be described below with reference to the accompanying drawings. The drawings are viewed in the direction of the reference numerals.
FIG. 1 is a cross-sectional view of a damper unit employing a variable damping force damper for a vehicle according to the present invention.
The damper unit 10 includes a damping force variable damper (shock absorber) 20, a coil spring 12, and an upper mount 13 that houses the coil spring 12 in the damping force variable damper 20 and supports the body (not shown) side. Consists of.

  The damping force variable damper 20 is slidably attached to the cylindrical cylinder 21, the piston 22 that divides the cylinder 21 into two chambers, and attached to the piston 22 from one end of the cylinder 21. Friction between the cylinder 21 and the piston 22, the rod 24 protruding through the rod guide 23, the damper oil 27 sealed in the cylinder 21 and flowing in two chambers through the orifices 25 and 26 of the piston 22 Friction generating means 50 for generating force, and a cover member 28 supported on the rod 24 side and covering the rod 24 and the cylinder 21.

The cover member 28 is supported on the rod 24 side by first to third damper rubbers 31 to 33.
The coil spring 12 is clamped between the upper mount 13 and the spring receiving portion 36 of the cylinder 21 by being fastened to the tip of the rod 24 with a nut 38 via a dish washer 34, a damper rubber 35, and a flat washer 37. The
The cylindrical cylinder 21 includes a wheel side support portion 39 that supports a wheel (not shown) side.

FIG. 2 is a sectional view of the friction generating means of the damping force variable damper of the vehicle shown in FIG.
The friction generating means 50 is disposed so as to be movable in the radial direction of the cylinder 21, and is disposed so as to be movable in the axial direction of the cylinder 21, and a shoe member 51 that applies a frictional force to the rod 24. The magnetically attracted member 52 that is moved in the axial direction, the support member 53 that supports the shoe member 51 in the axial direction of the rod 24 and that is slidable in the radial direction, and the attracted member 52 are disposed below. When the attracted member 52 moves in the axial direction of the cylinder 21, the shoe member 51 is moved to the cylinder 21. The electromagnetic coil 54 that attracts the attracted member 52 is interposed between the shoe member 51 and the attracted member 52. The leaf spring 55 that is moved in the radial direction of the head, and the shoe member 51 and the sucked member 52 are disposed on the upper surface of the plate spring 55 so that the shoe member 51 is slidably guided. A cushioning material (buffering member) 56 that shock-absorbs 2, a case 57 that collectively stores the shoe member 51, the attracted member 52, the electromagnetic coil 54, the leaf spring 55, and the cushioning material 56, and the case 57 And a lid member 59 attached via a packing 58.

The electromagnetic coil 54 includes an iron core 61 that attracts the member 52 to be attracted and a coil 62 provided on the iron core 61.
The case 57 includes a seal ring 64 that slidably supports the rod 24, and the lid member 59 includes a seal ring 63 that slidably supports the rod 24.

3 is an exploded perspective view of a shoe member and a leaf spring of the friction generating means shown in FIG. 2, FIG. 4 is a sectional view taken along line 4-4 of FIG. 3, and FIG. 5 is a line 5-5 of FIG. It is sectional drawing.
The shoe member 51 is a member in which a shoe piece 66 that is divided into four parts is arranged in a ring shape. The shoe piece 66 is a fitting groove 67 into which the leaf spring 55 is fitted, and a liner that applies frictional force to the rod 24. 68.

  The leaf spring 55 is a ring-shaped and dish-shaped disc spring (a disc spring with a slit). The through-hole 71 allows the plurality of shoe pieces 66 to face and the 4 provided continuously in the radial direction from the through-hole 71. From one divided groove 72, four divided pieces 73 divided by these divided grooves 72, and a fitting convex portion 74 to which a plurality of shoe pieces 66 are fitted by being formed in these divided pieces 73. Become.

6A and 6B are operation explanatory views for explaining the movement of the friction generating means shown in FIG.
In (a), since the electromagnetic coil 54 of the friction generating means 50 is in a non-excited state, the shoe member 51 is lifted upward as indicated by arrows a1 and a1 by a spring member, and the shoe member 51 is in a non-contact state with the rod 24. It is in. That is, if the diameter of the rod 24 is D1, the shoe member 51 is in a state in which the gaps S1 and S1 are maintained with respect to the rod 24. Therefore, the rod 24 is in a friction-free state from the shoe member 51.

  In (b), when the electromagnetic coil 54 of the friction generating means 50 is energized, the attracted member 52 is attracted as indicated by arrows b1 and b1 against the leaf spring 55, and the leaf spring 55 is changed from a plate shape to a ring shape (flat surface). Shape). As a result, the shoe member 51 is reduced in diameter as indicated by arrows b <b> 2 and b <b> 2, contacts the rod 24, and applies a frictional force to the rod 24.

  That is, as shown in FIG. 1, the damping force variable damper 20 is provided with a cylindrical cylinder 21, and a piston 22 that divides the cylinder 21 into two chambers is slidably attached to the cylinder 21. A rod 24 protruding from the cylinder 21 to the outside is attached to the piston 22, and a damper oil 27 that flows in two chambers through the orifices 25 and 26 of the piston 22 is sealed in the cylinder 21. Friction generating means 50 for generating a frictional force is provided.

  As shown in FIG. 2, the friction generating means 50 is a mechanism disposed on one end surface of the cylinder 21 and outside the cylinder 21, and the shoe member 51 is disposed so as to be movable in the radial direction of the cylinder 21. The magnetic member to be attracted 52 is disposed so as to be movable in the axial direction of the cylinder 21, and an electromagnetic coil 54 for attracting the attracted member 52 is disposed on the axial end surface of the cylinder 21 of the attracted member 52. A leaf spring 55 that moves the shoe member 51 in the radial direction of the cylinder 21 when the member 52 moves in the axial direction of the cylinder 21 is interposed between the shoe member 51 and the sucked member 52.

  That is, a leaf spring 55 that is interposed between the shoe member 51 and the sucked member 52 and moves the shoe member 51 in the radial direction of the cylinder 21 when the sucked member 52 moves in the axial direction of the cylinder 21 is employed. Therefore, for example, the structure is simplified and the assemblability is improved as compared with a case where a member such as a cam or a ball is used to perform the same operation. As a result, it is possible to simplify the structure of the damping force variable damper 20 of the vehicle.

  In the damping force variable damper 20, the friction generating means 50 is disposed on one end face of the cylinder 21 and outside the cylinder 21, so that it can be easily mounted on a damper having a conventional structure. As a result, the generalization of the friction generating means 50 can be promoted.

FIGS. 7A and 7B are comparative study diagrams of the vehicle damping force variable damper shown in FIG. 1, FIG. 7A shows a friction generating means 250 of a comparative example, and FIG. The friction generating means 50 is shown.
In (a), the friction generating means 250 is provided with a shoe member (sliding member) 252 that applies a friction force to the rod 251, and a magnetic member to be adsorbed that moves the shoe member 252 in the axial direction of the rod 251. 253 is provided, and when the attracted member 253 is moved in the axial direction of the rod 251, a cam surface 254 is provided for moving the shoe member 252 toward the center of the rod 251, and the shoe member 252 and the cam surface 254 are provided. Between which the ball 255 is provided, the electromagnetic coil 256 that attracts the attracted member 253 is provided, and the return spring 257 that biases the shoe member 252 against the attracting direction of the electromagnetic coil 256 is provided. This is a cam type friction generating means.

  Here, θ is the angle (wedge angle) formed by the center line of the rod 251 and the cam surface 254, F1 is the attractive force of the electromagnetic coil 256, F2 is the pressing force against the rod 251, and μ is the rod 251 and the shoe member (sliding). The frictional force Fr1 of the rod 251 can be described as Fr1 = μ · F2 = μ · F1 / tan θ when the dynamic friction coefficient with the moving member 252 and Fr1 is the frictional force of the rod 251. This 1 / tan θ is a factor that exerts a wedge boosting effect. For example, it is 11.4 times when θ = 5 °, 5.7 times when θ = 10 °, and 3 when θ = 15 °. .7 times the boost effect.

However, the friction generating means 250 is a ball-cam type friction generating means for applying a frictional force to the rod 251 with the shoe member 252, the cam surface 254, and the ball 255 as main components, and a structure that requires a return spring 257. For this reason, the structure becomes complicated. In particular, it is difficult to incorporate the ball 255 and the number of assembling steps increases.
Further, when the pressing force of the shoe member 252 is increased, there is a concern that self-locking may occur due to the “wedge structure” using the cam surface 254.
Further, the friction generating means 250 is a ball-cam type friction generating means for generating a rod pressing force due to a boosting effect by the “wedge structure”, and in order to avoid the self-locking, the friction generating means There may be constraints on 250 designs.

In (b), the friction generating means 50 is a disc spring type friction generating means with a slit including a shoe member 51, a member to be attracted 52, an electromagnetic coil 54, and a leaf spring 55.
Here, F3 is an attractive force of the electromagnetic coil 54, F4 is a pressing force against the rod 24, μ is a coefficient of dynamic friction between the rod 24 and the shoe member (sliding member) 52, k is a boost ratio of the leaf spring 55, Fr2 Is the frictional force of the rod 24, the frictional force Fr2 of the rod 24 can be described as Fr2 = μ · F4 = μ · F3 · k. In the actual design, the boost ratio k can be increased up to about 10.

  The friction generating means 50 is a disc spring type friction generating means with slits, which mainly includes a shoe member 51 and a leaf spring 55, and has a simple structure and can be easily assembled. For the same reason, it is possible to avoid the concern that the means for generating the frictional force is self-locking. Furthermore, since the structure that can avoid the concern of causing self-locking, the degree of freedom in design can be improved.

FIG. 8 is a graph showing an example of a change in the damping force characteristic of the vehicle damping force variable damper shown in FIG. 1 (see FIGS. 1 and 2 for the sign), the horizontal axis is the piston speed, and the vertical axis is the expansion side. And the damping force on the contraction side is shown.
A broken line T1 indicates a damping force characteristic with respect to the piston speed on the expansion side when the electromagnetic coil 54 is not excited, and a broken line C1 indicates a damping force characteristic with respect to the piston speed on the contraction side when the electromagnetic coil 54 is not excited. That is, the broken lines T1 and C1 are damper characteristics based only on the flow of the damper oil 27 as in a normal damper.

  Solid lines T2, T3, and T4 indicate damping force characteristics with respect to the piston speed on the extension side when the electromagnetic coil 54 is excited. The power (or voltage) of the solid line T2 is P2, and the power (or voltage) of the solid line T3 is P2. When the power (or voltage) of P3 and the solid line T4 is P4, the relationship of P2 <P3 <P4 is set. That is, as the voltage (electric power) exciting the electromagnetic coil 54 increases, the frictional force of the rod 24 also increases. That is, as shown by solid lines T2, T3, T4, the damping force on the extension side increases.

  Solid lines C2, C3, and C4 indicate damping force characteristics with respect to the contraction-side piston speed when the electromagnetic coil 54 is excited. The power (or voltage) of the solid line C2 is P2, the power (or voltage) of the solid line C3 is P3, When the power (or voltage) of the solid line C4 is P4, the relationship of P2 <P3 <P4 is set. That is, as the voltage (electric power) exciting the electromagnetic coil 54 increases, the frictional force of the rod 24 also increases. That is, as shown by the solid lines C2, C3, C4, the contraction-side damping force increases.

  In the damping force variable damper 20, by controlling the friction generating means 50, it is possible to effectively switch the roll rigidity and damping characteristics of the vehicle during normal traveling. Further, the friction generating means 50 can obtain a stable friction force, and can improve the stability of the damping force control. Furthermore, for example, even in the very low speed region S of about 0.1 m / sec, the damping force control by the friction generating means 50 is not prevented.

FIG. 9 is a graph showing an example of a change in the damping force characteristic when the minute amplitude of the damping force variable damper of the vehicle shown in FIG. 1 is vibrated (see FIG. 1 and FIG. 2 for the sign), and the horizontal axis Represents the piston speed, and the vertical axis represents the damping force on the expansion side and the contraction side.
A broken line T5 is a damping force characteristic with respect to the piston speed on the extension side when the electromagnetic coil 54 is in a non-excited state in the minute amplitude region of the piston 22 and at a very low piston speed, and shows a right-up characteristic. By generating a frictional force in the frictional force generating means 50, adjustment can be made as indicated by a solid line T6.

  A broken line C5 is a damping force characteristic with respect to the contraction-side piston speed when the electromagnetic coil 54 is in the non-excited state in the small amplitude region of the piston 22 and at a very low piston speed, and shows a downward-sloping characteristic. By generating a frictional force in the frictional force generating means 50, adjustment can be made as shown by a solid line C6.

FIG. 10 is a sectional view of a damper unit of a second embodiment of the variable damping force damper for a vehicle according to the present invention, and FIG. 11 is an enlarged view of part 11 of FIG.
The damping force variable damper 80 is a multi-cylinder damper. The cylinder 81 is slidably attached to the cylinder 81. The piston 82 divides the cylinder 81 into two chambers. A rod 84 that is attached and protrudes from one end of the cylinder 81 through a rod guide 83 and is sealed in the cylinder 81 and flows through two chambers through orifices 85 and 85 (one not shown) of the piston 82. 87, and friction generating means 90 that generates a frictional force between the cylinder 81 and the piston 82.

  The cylinder 81 includes an inner cylinder 88 on which the piston 82 slides, and an outer cylinder 89 provided coaxially with the inner cylinder 88 and on the outer side.

  The friction generating means 90 is a mechanism that is disposed inside the cylinder 81 from which the rod 84 extends, and is disposed so as to be movable in the radial direction of the cylinder 81, and a shoe member 91 that applies a frictional force to the rod 84; A magnetically attracted member 92 that is disposed so as to be movable in the axial direction of the cylinder 81 and moves the shoe member 91 in the axial direction of the rod 84, and supports the shoe member 91 in the axial direction of the rod 84 and in the radial direction A support cylinder 93 that is slidably supported, an electromagnetic coil 94 that is disposed below the member to be sucked 92 and sucks the member to be sucked 92, and is interposed between the shoe member 91 and the member to be sucked 92. A leaf spring 95 that moves the shoe member 91 in the radial direction of the cylinder 81 when the 92 moves in the axial direction of the cylinder 81, the shoe member 91, the sucked member 92, and the electric Coil 94, a case 97 for collectively accommodating the leaf spring 95, and a lid member 99 Metropolitan mounting via a packing 98 in this case 97.

The shoe member 91 is a member having substantially the same configuration as the shoe member 51 (see FIG. 3), and the leaf spring 95 is a member having substantially the same configuration as the leaf spring 55 (see FIG. 3).
The electromagnetic coil 94 includes an iron core 101 that attracts the member 92 to be attracted, and a coil 102 provided on the iron core 101.
The case 97 includes a seal ring 104 that slidably supports the rod 84, and the lid member 99 includes a seal ring 103 that slidably supports the rod 84.

  In the damping force variable damper 80, the friction generating means 90 is arranged inside the cylinder 81 from which the rod 84 extends. Thereby, the damping force variable damper 80 of a vehicle can be comprised compactly.

  In the damping force variable damper 80, the friction generating means 90 is disposed on the cylinder 81 side and the shoe member 91 is configured to press the outer peripheral surface of the rod 84. Therefore, the shoe member 91 can be small, and the friction generating means 90 Can be miniaturized.

FIG. 12 is a cross-sectional view of a damper unit of a third embodiment of a variable damping force damper for a vehicle according to the present invention, and FIG. 13 is an enlarged view of a portion 13 in FIG.
The damping force variable damper 110 is a multi-cylinder damper. The cylinder 111 is slidably attached to the cylinder 111. The piston 112 divides the cylinder 111 into two chambers. A rod 114 that is attached and protrudes from one end of the cylinder 111 through a rod guide 113 and a damper oil that is sealed in the cylinder 111 and flows through two chambers through orifices 115 and 115 (one not shown) of the piston 112. 117, and friction generating means 120 that generates a frictional force between the cylinder 111 and the piston 112.

  The cylinder 111 includes an inner cylinder 118 on which the piston 112 slides, and an outer cylinder 119 provided coaxially with the inner cylinder 118 and on the outer side.

The friction generating means 120 is a mechanism arranged inside the cylinder 111 (inner cylinder) from which the rod 114 is extended, and is arranged so as to be movable in the radial direction of the cylinder 111, and the friction force is applied to the cylinder 111 (inner cylinder). A shoe member 121 for imparting a magnetic force, a magnetically attracted member 122 for moving the shoe member 121 in the axial direction of the cylinder 111, and a shoe member 121 in the axial direction of the cylinder 111. And a support cylinder 123 that is slidably supported in the radial direction, an electromagnetic coil 124 that is disposed below the member to be sucked 122 and sucks the member to be sucked 122, and a shoe member 121 and a member to be sucked 122. When the sucked member 122 is moved in the axial direction of the cylinder 111, the shoe member 121 is moved in the radial direction of the cylinder 111. A plate spring 125 for moving, these shoe member 121, the suction member 122, the electromagnetic coil 124, a case 127 for collectively accommodating the plate spring 125,
A lid member 129 is attached to the case 127 via a packing 128.

The electromagnetic coil 124 includes an iron core 131 that attracts the member 122 to be attracted, and a coil 132 provided on the iron core 131.
The case 127 includes a seal ring (oil ring) 134 that slides slidably on the inner cylinder 118, and the lid member 129 includes a seal ring (oil ring) 133 that slides slidably on the inner cylinder 118.

  In the damping force variable damper 110, the friction generating means 120 is disposed on the rod 114 side, and the shoe member 121 is configured to press the inner surface of the cylinder 111. Therefore, the contact area of the shoe member 121 can be greatly increased. . As a result, a large frictional force can be generated between the cylinder 111 and the rod 114, and the performance of the variable damping force damper 110 of the vehicle can be improved.

  Note that the damping force variable dampers 20, 80, 120 of the vehicle according to the present invention may be single cylinder dampers or double cylinder dampers.

  The damping force variable dampers 20, 80, 120 of the vehicle according to the present invention may be ones in which lubricating oil is enclosed in cases 57, 97, 127.

  In the vehicular damping force variable damper 20 according to the present invention, the shoe member 51 is composed of the four shoe pieces 66, but the number may be any number. Further, the leaf spring 55 includes the divided pieces 73 divided into four parts, but may be divided by the number of shoe pieces.

  The vehicle damping force variable damper according to the present invention is suitable for use in passenger cars such as sedans and wagons.

It is sectional drawing of the damper unit which employ | adopted the damping force variable damper of the vehicle which concerns on this invention. It is sectional drawing of the friction generation means of the damping force variable damper of the vehicle shown by FIG. FIG. 3 is an exploded perspective view of a shoe member and a leaf spring of the friction generating means shown in FIG. 2. FIG. 4 is a cross-sectional view taken along line 4-4 of FIG. FIG. 5 is a sectional view taken along line 5-5 of FIG. It is operation | movement explanatory drawing explaining a motion of the friction generation means shown by FIG. FIG. 2 is a comparative study diagram of a variable damping force damper of the vehicle shown in FIG. 1. 2 is a graph showing an example of a change in damping force characteristics of the variable damping force damper of the vehicle shown in FIG. 1. It is a graph which shows an example of the change of the damping force characteristic when the very small amplitude of the damping force variable damper of the vehicle shown in FIG. 1 is vibrated. It is sectional drawing of the damper unit of 2nd Example of the damping-force variable damper of the vehicle which concerns on this invention. FIG. 11 is an enlarged view of part 11 in FIG. 10. It is sectional drawing of the damper unit of 3rd Example of the damping-force variable damper of the vehicle which concerns on this invention. FIG. 13 is an enlarged view of part 13 in FIG. 12. It is a figure explaining the basic composition of the conventional damping force variable damper.

Explanation of symbols

  20, 80, 110 ... damping force variable damper, 21, 81, 111 ... cylinder, 22 ... piston, 24, 84, 114 ... rod, 25, 26 ... orifice, 27 ... damper oil, 50, 90, 120 ... friction Generation means, 51, 91, 121 ... shoe member, 52 ... attracted member, 54 ... electromagnetic coil, 55 ... leaf spring.

Claims (5)

A cylindrical cylinder, a piston slidably attached to the cylinder and partitioning the cylinder into two chambers, a rod attached to the piston and projecting outward from the cylinder, and sealed in the cylinder; A damper for a vehicle with a variable damping force, comprising a damper oil flowing through the two chambers through an orifice of a piston, and a friction generating means for generating a frictional force between the cylinder and the rod,
The friction generating means includes a shoe member disposed so as to be movable in a radial direction of the cylinder, a magnetically attracted member disposed so as to be movable in an axial direction of the cylinder, and the cylinder of the attracted member. An electromagnetic coil disposed on an end face in the axial direction and interposed between the electromagnetic coil for attracting the attracted member, the shoe member and the attracted member, and when the attracted member moves in the axial direction of the cylinder, A damper for a variable damping force of a vehicle, comprising a leaf spring for moving a shoe member in a radial direction of the cylinder.   2. The variable damping force damper for a vehicle according to claim 1, wherein the friction generating means is disposed on one end surface of the cylinder and outside the cylinder.   2. The variable damping force damper for a vehicle according to claim 1, wherein the friction generating means is disposed inside the cylinder from which the rod extends.   4. The vehicular damping force variable damper according to claim 3, wherein the friction generating means is disposed on the cylinder side, and the shoe member presses an outer peripheral surface of the rod.   4. The vehicular damping force variable damper according to claim 3, wherein the friction generating means is disposed on the rod side, and the shoe member presses the inner surface of the cylinder.

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