Suspension system

Abstract: The posture of a vehicle is controlled using a specific variable damping force damper without the necessity of changing over the variable damping force damper frequently and at a high rate and without using a vehicle height sensor. A variable damping force damper U having at least two change-over modes including a mode in which the compression side damping force is soft when the extension side damping force is hard and another mode in which the compression side damping force is hard when the extension side damping force is soft is interposed between a vehicle body D and a wheel E. The variable damping force damper U is changed over by means of an acceleration sensor J mounted on the vehicle body D and a controller M including an integrator P for converting a signal from the acceleration sensor J into a velocity signal and a calculation processing circuit Q for outputting a changing over signal to the variable damping force damper U in accordance with the velocity signal from the integrator P.

Description: This invention relates to a suspension system which changes the damping force generated from a damper appropriately in response to vibrations produced on the body of a vehicle to control the posture (i.e. the position, attitude and movement) of the vehicle body. A suspension for a travelling vehicle does not provide satisfactory driving feeling if it merely damps and absorbs vibrations produced on the body of the vehicle. In order to achieve further improvement in driving feeling, it is desirable to employ a suspension of the active control type which detects behaviour characteristics of the vehicle body to control the vehicle body so as to positively maintain an appropriate posture thereof. However, the active suspension system requires a hydraulic pump and a hydraulic valve and is complicated, particularly in the construction of its controller for controlling the pump and valve. Consequently, it is of high cost. Thus, increasing attention is paid to a so-called semi-active suspension system wherein a damper which has a variable damping force is employed so that the damping force characteristic is automatically controlled in response to an amplitude or a frequency of vibrations of the vehicle body. Fig. 6 shows a basic construction of a conventional semi-active suspension system for a vehicle having four wheels. Referring to Fig. 6, the semi-active suspension system shown is constructed for a single wheel for the convenience of illustration and description. Such a semi-active suspension system is in practice provided for each of the four wheels of the vehicle and only a controller is provided commonly for the semi-active suspension systems for the four wheels. A suspension spring F, a known variable damping force damper G having a damping force which can be changed over between two hard and soft modes, and a vehicle height sensor H are interposed between a vehicle body D and a wheel E. An acceleration sensor J for detecting a vertical acceleration of the vehicle body D is provided on the vehicle body D. A tire L serving as a spring element is present between the wheel E and the ground K. A controller M includes a differentiator N, an integrator P and a calculation processing circuit Q. A signal from the vehicle height sensor H is inputted to the differentiator N while a signal from the acceleration sensor J is inputted to the integrator P. The calculation processing circuit Q processes output signals of the differentiator N and the integrator P and provides a damping force changing over signal to the variable damping force damper G so that the damping force may be changed over between two hard and soft stages on each of the extension and contraction sides of the variable damping force damper G as seen from Fig. 7. As can be seen also from the basic construction described above, the controlling method of the conventional semi-active suspension system proceeds in the following manner. In particular, where the displacements of the vehicle body D and the wheel E are represented by x and y, respectively, when the directions indicated by arrow marks in Fig. 6 are assumed to be positive in sign for the convenience of description, the relative velocity x ˙ - y ˙ between the vehicle body D and the wheel E is obtained by differentiating a signal x - y of the vehicle height sensor H by means of the differentiator N of the controller M. Meanwhile, the velocity x ˙ of the vehicle body D is obtained by integrating a signal x of the acceleration sensor J by means of the integrator P of the controller M. Here, if attention is paid to the damping force of the variable damping force damper G acting upon the vehicle body D, when x ˙ > 0 whereby the vehicle body D is moving upwardly and x ˙ - y ˙ > 0, then the variable damping force damper G is performing an extending operation and, accordingly, the damping force thus generated acts in the direction opposite to the direction of the movement of the vehicle body D. Consequently, the extension side damping force then acts as a vibration controlling force upon the vehicle body D. However, if x ˙ - y ˙ < 0, then the damping force generated acts in the same direction as the direction of the movement of the vehicle body D and, consequently, the compression side damping force then acts as a vibration promoting force upon the vehicle body D. Similarly, also when x ˙ < 0 whereby the vehicle body D is moving downwardly and x ˙ - y ˙ < 0, the variable damping force damper G performs a compressing operation, the compression side damping force then acts as a vibration controlling force upon the vehicle body D. On the contrary, in the case of x ˙ - y ˙ > 0 whereby the variable damping force damper G performs an extending operation, the extension side damping force then acts as a vibration promoting force upon the vehicle body D. If this is represented in four quadrants taking x ˙ and x ˙ - y ˙ as the axis of ordinate and the axis of abscissa, respectively, then as seen in Fig. 8 the variable damping force damper G provides a vibration controlling force to the vehicle body D in the first and third quadrants, but provides a vibration promoting force to the vehicle body D in the second and fourth quadrants. The vibration controlling force acts so as to control vibrations of the vehicle body D upon vibration of the wheel E, and on the contrary the vibration promoting force acts so as promote vibrations of the vehicle body D upon vibration of the wheel E. Accordingly, as seen from Fig. 9, if the variable damping force damper G is changed over, in the first and third quadrants, to a hard mode in which the generated damping force is high or, in the second and fourth quadrants, to a soft mode in which the generated damping force is low, then vibrations of the vehicle body D can be controlled to a low level against vibrations of the vehicle E. If this is represented algebraically, then: when x ( x - y ) > 0 → hard damping force; and when x ( x - y ) < 0 → soft damping force. The driving feeling of the vehicle can be improved by controlling the variable damping force damper G in this manner. However, with the conventional suspension system described above, while generally the sign of x ˙ of the vehicle body D varies at a natural frequency, e.g. at one hertz, which depends upon the mass of the vehicle body and the spring constant of the suspension spring F, the sign of the relative velocity x ˙ - y ˙ between the vehicle body D and the wheel E varies at a considerably higher frequency in response to an instantaneous input of force from the ground K, resonance between the wheel E and the tire L, and so forth. As a result, since the variable damping force damper G must necessarily be changed over at a high frequency between the hard and soft levels, considerable durability is required for the variable damping force damper itself and also for a changing over actuator for it. Besides, if the actuator is not changed over at a high speed, then the controlling effect is deteriorated. Further, since the relative velocity x ˙ - y ˙ between the vehicle body D and the vehicle E must necessarily be detected, a vehicle height sensor H must be provided for each of the wheels E. Accordingly, there is a problem that the entire system has a high cost. EP-A-0221602 discloses a variable damping force damper which has three damping modes. The document discloses a first mode (see Fig. 1) with a medium extension damping force and a soft compression damping force, a second mode (see Fig. 2) with a soft extension damping force and a soft compression damping force, and a third mode (see Fig. 3) with a hard extension damping force and a hard compression damping force. According to the present invention, there is provided a suspension system for a vehicle, comprising: a variable damping force damper interposable between a vehicle body and a wheel, said variable damping force damper having modes R and C with different compression/extension damping force characteristics; an acceleration sensor mountable on the vehicle body for measuring acceleration of the vehicle body along the compression/extension axis of said damper and for generating an acceleration signal; and a controller including an integrator for integrating said acceleration signal into a velocity signal and a calculation processing circuit for switching said damper between said mode R and said mode C; characterised in that: said damper is arranged so that the compression damping force is softer in said mode R than in said mode C and the extension damping force is harder in said mode R than in said mode C; and said calculation processing circuit is arranged to set said damper in said mode R when said velocity signal is on one side of zero and to set said damper in said mode C when said velocity signal is on the other side of zero. Thus, there is provided a suspension system wherein a variable damping force damper need not be changed over frequently or at a high speed and a vehicle height sensor is not required. It is possible to operate the suspension system by using only the vibration velocity of the vehicle body to effect posture control of the travelling vehicle. Consequently, the variable damping force damper need not be changed over frequently or at a high rate. Accordingly, the durability of the entire system is enhanced significantly. Besides, a vehicle height sensor is unnecessary, and accordingly the entire system can be constructed at a reduced cost. Preferably, both the extension and compression damping forces can be changed over to a soft level, to give a good driving feeling of the vehicle when high frequency vibrations occur during travelling on a good road. Furthermore, the variable damping force damper for the suspension system can be made so that the changing over between the modes R and C can be performed smoothly by making the compression damping force characteristics in the modes close to each other. Besides, since a mode in which both the extension and compression damping forces are soft can be added, the enhancement of driving feeling during high frequency vibrations during driving on a good road can be achieved. There now follows a description of a preferred embodiment of the invention, by way of example, with reference to being made to the accompanying drawings, in which: Fig. 1 is a diagrammatic view of a suspension system according to the present invention; Fig. 2 is a graph showing damping force characteristics of a variable damping force damper employed in the suspension system; Fig. 3 is a vertical sectional front elevational view showing an embodiment of the variable damping force damper; Fig. 4 is an enlarged vertical sectional front elevational view showing details of a valve structure of a piston of the variable damping force damper of Fig. 3; Fig. 5 is a schematic view showing open and closed conditions of communicating holes of a rotary valve in different modes of the variable damping force damper; Fig. 6 is a diagrammatic view of a conventional suspension system; Fig. 7 is a graph showing damping force characteristics of a variable damping force damper employed in the suspension system of Fig. 6. Fig. 8 is a schematic view illustrating different forces of the variable damping force damper of Fig. 6 acting upon a body of a vehicle; and Fig. 9 is a similar view but illustrating a rule of control based on a force of the variable damping force damper of Fig. 6 acting upon the body of the vehicle. Figs. 1 to 5 show an embodiment of the present invention. Referring first to Fig. 1, a so-called semi-active suspension system, which is a form of a suspension system, includes a suspension spring F and a variable damping force damper U interposed between a vehicle body D and a wheel E. Meanwhile, a tire L serving as a spring element is present between the wheel E and the ground K. An acceleration sensor J for detecting a vertical acceleration of the vehicle body D is provided on the vehicle body D. A controller M receives a signal from the acceleration sensor J and controls the damping force to be generated from the variable damping force damper U. The controller M includes an integrator P and a calculation processing circuit Q. A signal from the acceleration sensor J provided on the vehicle body D is inputted to the integrator P, and the calculation processing circuit Q processes the output signal of the integrator P and provides a damping force changing over signal to the variable damping force damper U so that the damping force to be generated from the variable damping force damper U is changed between three modes including a mode C, another mode S and a further mode R illustrated in Fig. 2. As can be seen also from the basic construction described above, the semi-active suspension system differs from the conventional suspension system described hereinabove at least in that it eliminates the vehicle height sensor H interposed between the vehicle body D and the wheel E and the differentiator N in the controller M and includes the variable damping force damper U which is different from the variable damping force damper G. Referring to Figs. 3 and 4, the variable damping force damper U employed in the present semi-active suspension system includes a cylinder 1 in the form of an enclosed tube, a piston 2 inserted for sliding movement in the cylinder 1, an outer shell 3 cooperating with the cylinder 1 to define a reservoir chamber T therebetween, and a piston rod 4 carrying the piston 2 thereon. The piston 2 is securely fastened to a faucet portion at a lower end of the piston rod 4 by means of a piston nut 5, and the inside of the cylinder 1 is partitioned by the piston 2 into an upper operating oil chamber A on the rod side and a lower operating oil chamber B on the head side. The piston rod 4 extends outwardly through a bearing 6 and a seal 7 both provided at an upper portion of the cylinder 1 while an eye 8 is welded to the lower end of the cylinder 1. The upper end of the piston rod 4 is connected to the vehicle body and the eye 8 is connected to the the wheel E. A base valve 9 is provided at a lower portion in the cylinder 1 and partitions the lower operating oil chamber B and the reservoir chamber T from each other. The base valve 9 includes a check valve 10 for admitting operating oil in the reservoir chamber T into the lower operating oil chamber B during the extension stroke of the variable damping force damper U, and a compression side valve 11 of the inner periphery fixed type for providing resistance to operating oil flowing from the lower operating oil chamber B toward the reservoir chamber T during the compression stroke to raise the pressure of operating oil in the lower operating oil chamber B. The piston 2 has an extension side port 12 and a compression side port 13 perforated therein for communicating the upper operating oil chamber A and the lower operating oil chamber B with each other. A lower end exit of the extension side port 12 is normally closed with an extension side main valve 14 of the inner periphery fixed type which is normally urged by a spring 14a interposed between the piston nut 5 and the piston 2. Similarly, an upper end exit of the compression side port 13 is normally closed with a compression side main valve 15 of the inner periphery fixed type. The piston rod 4 carrying the piston 2 thereon is hollow and defines a bypass passage 16 therein. The bypass passage 16 is communicated at a lower end thereof with the lower operating oil chamber B in the cylinder 1. A control rod 17 and a rotary valve 18 are accommodated in the bypass passage 16 and are coupled to each other to generally form a change-over valve. The rotary valve 18 may naturally be replaced by a sliding valve disposed for upward and downward sliding movement. The control rod 17 and the rotary valve 18 are stopped by a letting off preventing stopper 19 located below them and force fitted in the bypass passage 16. The control rod 17 is connected at an upper end thereof to an actuator 47 in order to change over the rotary valve 18, and an instruction signal from the controller M is provided to the actuator 47. Provided in a layered condition above the piston 2 are an extension side bypass passage mechanism 20, a compression side bypass passage mechanism 21 and an extension-compression bypass passage mechanism 22. The three mechanisms 20 to 22 are securely fastened to the faucet portion at the lower end of the piston rod 4 together with the piston 2 by the piston nut 5. As can be seen from the detailed view of the piston shown in Fig. 4, the extension side bypass passage mechanism 20 plays the role of providing a flow of operating oil which bypasses the piston 2 during the extension stroke of the variable damping force damper U and flows from the upper operating oil chamber A side to push open the extension side bypass valve 27 to generate the extension side damping force, whereafter it flows into the lower operating oil chamber B side. On the other hand, the compression side bypass passage mechanism 21 plays the role of providing a bypass flow of operating oil which bypasses the piston 2 during the compression stroke of the variable damping force damper U and flows from the lower operating oil chamber B side to push open a compression side bypass valve 36 to generate the compression side damping force, whereafter it flows to the upper operating oil chamber A side. Meanwhile, the extension-compression bypass passage mechanism 22 provides a bypass flow of operating oil which bypasses the piston 2 whether the variable damping force damper is in the extension stroke or the compression stroke and flows between the upper operating oil chamber A and the lower operating oil chamber B. The extension side bypass passage mechanism 20 includes a partition wall member 24 having a passage 23 formed therein, a valve stopper 25, a spacer 26, an extension side bypass valve 27 of the inner periphery fixed type, and a valve seat member 29 having formed therein an extension side bypass passage 28 which is closed at the opening at a lower end thereof with the extension side bypass valve 27. Those elements are accommodated in a piled up condition in a casing 30. Similarly, the compression side bypass passage mechanism 21 includes a partition wall member 32 having a passage 31 formed therein, and a valve seat member 34 having a compression side bypass passage 33 formed therein. The partition wall member 32 and the valve seat member 34 are accommodated in a casing 35. The compression side bypass passage mechanism 21 further includes a compression side bypass valve 36 of the inner periphery fixed type which closes the opening at a lower end of the compression side bypass passage 33, a spacer 37 and a valve stopper 38. The compression side bypass valve 36, the spacer 37 and the valve stopper 38 are piled up successively below the casing 35. Meanwhile, the extension-compression bypass passage mechanism 22 has an extension-compression bypass passage 40 formed by covering a recess, which is formed in a lower face of the valve stopper 38 of the compression side bypass passage mechanism 21, with a valve stopper 39 of the compression side valve 15 of the piston 2. On the other hand, the piston rod 4 has an extension side communicating hole 41 and a compression side communicating hole 42 as well as an extension-compression orifice communicating hole 43 perforated therein such that they face the passages 23 and 31 of the extension and compression side bypass passage mechanisms 20 and 21 as well as the extension-compression bypass passage 40 of the extension-compression bypass passage mechanism 22, respectively. Further, the rotary valve 18 has three through-holes 44, 45 and 46 formed therein for opening and closing the extension side communicating hole 41, the compression side communicating hole 42 and the extension-compression orifice communicating hole 43, respectively. The through-holes 44, 45 and 46 of the rotary valve 18 are provided in a displaced relationship in phase in the W-W section, the X-X section and the Y-Y section of Fig. 4 so that, usually, a total of three modes including a mode R, another mode S and a further mode C can be achieved as shown in Fig. 5. In particular, in the mode R, only the compression side communicating hole 42 is open; in the mode S, all of the extension side communicating hole 41, the compression side communicating hole 42 and the extension-compression orifice communicating hole 43 are open; and, in the mode C, only the extension side communicating hole 41 is open. It is to be noted that, when the rotary valve 18 is rotated in the clockwise direction to change over the mode from the mode S to the mode R, the extension side communicating hole 41 and the extension-compression orifice communicating hole 43 are gradually closed while the compression side communicating hole 42 remains open. Similarly, when the rotary valve 18 is rotated in the counterclockwise direction to change over the mode from the mode S to the mode C, the compression side communicating hole 42 and the extension-compression orifice communicating hole 43 are gradually closed while the extension side communicating hole 41 remains open. When necessary, finer control can be achieved by providing one or more positions of the rotary valve 18 between the positions for the mode S and the mode R and between the positions for the mode S and the mode C. Further, the width of control is increased by suitably selecting the displacement in phase of the extension-compression orifice communicating hole 43 from the extension and compression side communicating holes 41 and 42. Now, operation of the suspension system will be described. First, operation of the variable damping force damper U interposed between the vehicle body D and the wheel E will be described for the convenience of description. The damping force damper U operates in the following manner in the modes established by a changing over operation of the rotary valve 18. (1) Mode R During the extension stroke, operating oil in the upper operating oil chamber A flows only from the extension side port 12 of the piston 2 into the lower operating oil chamber B while pushing open the extension side main valve 14 to generate a damping force, and an amount of operating oil which corresponds to a volume by which the piston rod 4 is retracted is supplied from the reservoir chamber T into the lower operating oil chamber B while pushing open the check valve 10 of the base valve 9. On the other hand, during the compression side stroke, an amount of operating oil which corresponds to a volume by which the piston rod 4 is advanced flows from the lower operating chamber B into the reservoir chamber T while pushing open the compression side valve 11 of the base valve 9 to raise the pressure of operating oil in the lower operating oil chamber B. The operation oil of the raised pressure flows, since the cracking pressure of the compression side bypass valve 36 is lower than that of the compression side main valve 15 of the piston 2, through the bypass passage 16 of the piston rod 4 and then through the through-hole 45 of the rotary valve 18 and the compression side communicating hole 42 of the piston rod 4 and then flows through the compression side bypass passage 33 into the upper operating oil chamber A while pushing open the compression side bypass valve 36 to generate a damping force. Accordingly, in the mode R, a hard damping force is generated on the extension side, and a soft damping force is generated on the compression side. (2) Mode C During the extension stroke, operating oil in the upper operating oil chamber A flows through the extension side bypass passage 28 and pushes open the extension side bypass valve 27, the cracking pressure of which is lower than that of the extension side main valve 14 of the piston 2, to generate a damping force. The operating oil further flows through the extension side communication hole 41 of the piston rod 4 and the through-hole 44 of the rotary valve 18 and then through the bypass passage 16 into the lower operating oil chamber B. Further, an amount of operating oil corresponding to a volume by which the piston rod 4 is retracted is supplied from the reservoir chamber T into the lower operating oil chamber B while pushing open the check valve 10 of the base valve 9. On the other hand, during the compression stroke, an amount of operating oil which corresponds to a volume by which the piston rod 4 is advanced flows from the lower operating oil chamber B into the reservoir chamber T while pushing open the compression side valve 11 of the base valve 9 to raise the pressure of the operating oil in the lower operating oil chamber B. The operating oil of the thus raised pressure flows into the upper operating oil chamber A while pushing open the compression side main valve 15 of the piston 2 to generate a damping force. Accordingly, in the mode C, contrary to the mode R described above, a soft damping force is generated on the extension side, and a hard damping force is generated on the compression side. (3) Mode S During the extension stroke, when the piston 2 moves at a low speed, operating oil in the upper operating oil chamber A flows through the extension-compression bypass passage 40, the extension-compression orifice communicating hole 43 of the piston rod 4 and the through-hole 46 of the rotary valve 18 while generating a damping force by a pressure difference appearing at the extension-compression orifice communicating hole 43. The operating oil further flows through the bypass passage 16 into the lower operating oil chamber B. On the other hand, when the piston 2 moves at an intermediate or high speed, another flow of operating oil is produced in parallel to the flow of operating oil described above. In particular, operating oil flows through the extension side bypass passage 28 and pushes open the extension side bypass valve 27 to generate a damping force. The operating oil further flows through the extension side communicating hole 41 of the piston rod 4, the through-hole 44 of the rotary valve 18 and the bypass passage 16 into the lower operating oil chamber B. Further, an amount of operating oil which corresponds to a volume by which the piston rod 4 is retracted is supplied from the reservoir chamber T into the lower operating oil chamber B while pushing open the check valve 10 of the base valve 9. On the other hand, during the compression stroke, an amount of operating oil which corresponds to a volume by which the piston rod 4 is advanced flows from the lower operating oil chamber B into the reservoir chamber T while pushing open the compression side main valve 11 of the base valve 9 to raise the pressure of the operating oil in the lower operating oil chamber B. When the piston 2 moves at a low speed, the operating oil of the raised pressure flows through the bypass passage 16, the through-hole 46 of the rotary valve 18 and the extension-compression orifice communicating hole 43 of the piston rod 4 while generating a damping force by a pressure difference appearing at the extension-compression orifice communicating hole 43. The operating oil further flows through the extension-compression bypass passage 40 into the upper operating oil chamber A. However, when the piston moves at an intermediate or high speed, another flow of operating oil is produced in parallel to the flow of operating oil just described. In particular, operating oil flows through the bypass passage 16, the through-hole 45 of the rotary valve 18 and the compression side communicating hole 42 of the piston rod 4 and further flows through the compression side bypass passage 33 into the upper operating oil chamber A while pushing open the compression side bypass valve 36 to generate a damping force. Accordingly, in the mode S, a softer damping force than the soft damping force on the compression side in the mode R and the soft damping force on the extension side in the mode C is generated. Now, control of the semi-active suspension system will be described. While the controlling means of the conventional semi-active suspension system described hereinabove controls such that, when x ˙ > 0, a hard damping force is generated if x ˙ - y ˙ > 0, but a soft damping force is generated if x ˙ - y ˙ < 0, this is because it is necessary to change over the damping force in accordance with the positive or negative sign of "x ˙ - y ˙" since, when the variable damping force damper G generates a hard damping force during the extension stroke, it generates a hard damping force also during the compression stroke. On the other hand, if the variable damping force damper U of the embodiment described above is employed, then when a hard damping force is generated during the extension stroke a soft damping force is generated automatically during the compression stroke, and when a hard damping force is generated during the compression stroke a soft damping force is generated automatically during the extension stroke. Accordingly, there is no necessity of changing over the damping force in accordance with the positive or negative sign of x ˙ - y ˙. When x ˙ > 0, the mode is set to the mode R so that the extension side damping force may be controlled to a hard damping force, but when x ˙ < 0 the mode is changed over to the mode C so that the compression side damping force may be controlled to a hard damping force. In this manner, similar control effects to those of the conventional semi-active suspension system can be exhibited only by selecting the mode R or the mode C in accordance with the positive or negative sign of the velocity x ˙ of the vehicle body D irrespective of the relative velocity x ˙ - y ˙ between the vehicle body D and the wheel E. Besides, since the transition between the positive and negative signs of the velocity x ˙ of the vehicle body D is comparatively slow oscillations of 1 Hz or so, sufficient control effect can be obtained even if the damping force changing over rate of the actuator 47 is not very high, and besides the changing over frequency may be low. Meanwhile, when the input frequency from the road K becomes a high frequency, the transmission of the force to the vehicle body D is reduced and the driving feeling is improved when the damping force is decreased. Thus, when the input frequency becomes high, since the velocity x ˙ of the vehicle body D is decreased, the mode is changed over to the mode S in which a soft damping force is generated during both the extension and the compression strokes. By the control described above, the changing over frequency of the variable damping force damper U can be decreased and the driving feeling can be improved without increasing the changing over rate very much. In the above embodiment, it is not necessary to change over the variable damping force damper frequently and at a high rate. Consequently, there is the effect that the durability of the suspension system is enhanced. Besides, since a vehicle height sensor is unnecessary, there is another effect that the system itself can be constructed at a low cost. Further, because the extension side damping force and the compression side damping force can both be changed over to a soft level, there is a good driving feeling upon occurrence of high frequency vibrations upon travelling on a good road or the like.

Claims: A suspension system for a vehicle, comprising: a variable damping force damper (U) interposable between a vehicle body (D) and a wheel (E), said variable damping force damper (U) having modes R and C with different compression/extension damping force characteristics; an acceleration sensor (J) mountable on the vehicle body (D) for measuring acceleration of the vehicle body along the compression/extension axis of said damper (U) and for generating an acceleration signal (x ¨); and a controller (M) including an integrator (P) for integrating said acceleration signal (x ¨) into a velocity signal (x ˙) and a calculation processing circuit (Q) for switching said damper (U) between said mode R and said mode C; characterised in that: said damper (U) is arranged so that the compression damping force is softer in said mode R than in said mode C and the extension damping force is harder in said mode R than in said mode C; and said calculation processing circuit (Q) is arranged to set said damper (U) in said mode R when said velocity signal (x ˙) is on one side of zero and to set said damper (U) in said mode C when said velocity signal (x ˙) is on the other side of zero. A suspension system according to claim 1, wherein: said variable damping force damper (U) has a mode S in which the compression damping force is softer than the mode R compression damping force and the extension damping force is softer than the mode C extension damping force; and said calculation processing circuit (Q) is arranged to set said damper (U) in said mode S when said velocity signal (x ˙) has a low value. A suspension system according to claim 1 or 2, wherein: said integrator (P) is arranged to give said velocity signal (x ˙) a positive sign for upward movement of said acceleration sensor (J) and a negative sign for downward movement of said acceleration sensor (J); and said calculation processing circuit (Q) is arranged to set said damper (U) in said mode R when said velocity signal (x ˙) is positive and to set said damper (U) in said mode C when said velocity signal (x ˙) is negative. A suspension system according to claim 2 or claims 2 and 3, wherein said variable damping force damper (U) comprises: a cylinder (1) containing a piston (2) which separates said cylinder into an upper operating oil chamber (A) and a lower operating oil chamber (B); said piston (2) having an extension port (12) and a compression port (13) for communicating said upper operating oil chamber (A) and said lower operating oil chamber (B) with each other, and an extension main valve (14) and a compression main valve (15) which cooperate with said extension and compression ports, respectively; an extension bypass passage (23), a compression bypass passage (31) and an extension-compression bypass passage (40) all disposed in parallel to said extension and compression ports (12, 13) for individually communicating said upper operating oil chamber (A) and said lower operating oil chamber (B) with each other; an extension bypass valve (27) and a compression bypass valve (36) which cooperate with said extension and compression bypass passages (23, 31), respectively; and a change-over valve (18) having change-over positions including a position in which only said extension bypass passage (23) is open, another position in which only said compression bypass passage (31) is open, and a further position in which all of said extension and compression bypass passages (23, 31) and said extension-compression bypass passage (40) are open. A suspension system according to claim 2 or claims 2 and 3, wherein: said variable damping force damper (U) includes a piston rod (4) having an extension communicating hole (41), a compression communicating hole (42) and an extension-compression orifice communicating hole (43) formed therein, and a rotary valve (18) inserted in said piston rod (4) and having three through-holes (44, 45, 46) formed therein for selectively opening and closing said extension communicating hole (41), said compression communicating hole (42) and said extension-compression orifice communicating hole (43); said calculation processing circuit (Q) being arranged to set said damper (U) in said mode C by rotating said rotary valve (18) to open said extension communicating hole (41) while closing the other communicating holes (42, 43); said calculation processing circuit (Q) being arranged to set said damper (U) in said mode R by rotating said rotary valve (18) to open said compression communicating hole (42) while closing the other communicating holes (41, 43); and said calculation processing circuit (Q) being arranged to set said damper (U) in said mode S by rotating said rotary valve (18) to open said three communicating holes (41 42, 43). A suspension system according to any one of claims 1 to 3, wherein said variable damping force damper (U) comprises: a cylinder (1) containing a piston (2) which separates said cylinder into an upper operating oil chamber (A) and a lower operating oil chamber (B); said piston (2) having an extension port (12) and a compression port (13) for communicating said upper operating oil chamber (A) and said lower operating oil chamber (B) with each other, and an extension main valve (14) and a compression main valve (15) which cooperate with said extension and compression ports, respectively; an extension bypass passage (23) and a compression bypass passage (31) both disposed in parallel to said extension and compression ports (12, 13) for individually communicating said upper operating oil chamber (A) and said lower operating oil chamber (B) with each other; an extension bypass valve (27) and a compression bypass valve (36) which cooperate with said extension and compression bypass passages (23, 31), respectively; and a change-over valve (18) having change-over positions including a position in which only said extension bypass passage (23) is open, another position in which only said compression bypass passage (31) is open, and a further position in which both of said extension and compression bypass passages (23, 31) are open. A suspension system according to claim 1 or claims 1 and 3, wherein: said variable damping force damper (U) includes a piston rod (4) having an extension communicating hole (41) and a compression communicating hole (42) formed therein, and a rotary valve (18) inserted in said piston rod (4) and having two through-holes (44, 45) formed therein for selectively opening and closing said extension communicating hole (41) and said compression communicating hole (42); said calculation processing circuit (Q) being arranged to set said damper (U) in said mode C by rotating said rotary valve (18) to open said extension communicating hole (41) while closing said compression communicating hole (42); and said calculation processing circuit (Q) being arranged to set said damper (U) in said mode R by rotating said rotary valve (18) to close said extension communicating hole (41) while opening said compression communicating hole (42). A vehicle including a suspension system according to any one of claims 1 to 7, wherein said damper (U) is interposed between a vehicle body (D) and a wheel (E) and said acceleration sensor (J) is mounted on said vehicle body (D).

Inventors: KITAMURA KENJI, MASAMURA TATSUYA, MIZUMUKAI KEN, TAKASE KOJI, KITAMURA, KENJI, MASAMURA, TATSUYA, MIZUMUKAI, KEN, TAKASE, KOJI, MIZUMUKAI, KEN, 60-305 IWAKURADANCHI
Applicants: KAYABA INDUSTRY CO LTD, KAYABA KOGYO KABUSHIKI KAISHA
Application year: 1992
Main classification: B60G17
IPC codes: F16F9, B60G17