Active suspension assembly for a vehicle

• US 8,308,170 B2
• Filed: 10/23/2007
• Issued: 11/13/2012
• Est. Priority Date: 10/23/2006
• Status: Expired due to Fees

• Current Assignee: Nederlandse Organisatie Voor Toegepast-Natuurwetenschappelijk Onderzoek Tno
• Original Assignee: Nederlandse Organisatie Voor Toegepast-Natuurwetenschappelijk Onderzoek Tno
• Inventors: Van Der Knaap, Albertus Clemens Maria, Teerhuis, Arjan Pieter, Tinsel, Raymond Bernardus Gerhardus, Verschuren, Robert Marijn Anthony Frank
• Primary Examiner(s): Culbreth, Eric
• Application Number:
  US12/446,474
• Publication Number:
  US 20100301571A1
• Time in Patent Office: 1,848 Days
• Field of Search: 280/5.507, 280/5.508, 280/5.5
• US Class Current: 280/5.507
• CPC Class Codes: B60G 17/0152 characterised by the action on a particular type of suspension unit B60G17/01941 takes precedence
• CPC Class Codes: B60G 17/021 the mechanical spring being a coil spring B60G17/0272 takes precedence
• CPC Class Codes: B62D 33/0604 Cabs insulated against vibrations or noise, e.g. with elastic suspension resilient connections between superstructure sub-units B62D27/04; damping noise in general G10K11/00; for vehicles in general B60R13/08

Abstract

The invention relates to an active suspension assembly and a vehicle equipped therewith. The assembly comprises a bearing arm, spring and adjusting mechanism. In use, the bearing arm supports the second vehicle mass, for instance a cabin or wheel and is pivotally connected to the first vehicle mass, for instance a chassis, around a pivot axis; the spring mechanism produces a spring force that exerts a counter moment on the bearing arm that can counterbalance any external moment acting on said bearing arm; and the adjustment mechanism is arranged to vary said counter moment by altering the direction of the spring force and/or move its point of application in a first direction. The adjustment mechanism is furthermore arranged to move the point of application of the spring force in a second direction, in which the counter moment is not or hardly affected, but by which the effective spring stiffness of the suspension assembly is affected. Thanks to said latter movement, the effective stiffness of the suspension can be maintained at a desired value.

Claims

1. Active suspension assembly (1, 101) for use in a vehicle to suspend a second vehicle mass (6, 106) to a first vehicle mass (4, 104), the assembly (1, 101) comprising a bearing arm (3, 103), spring means (5, 105) and adjustment means (110), wherein in use:

the bearing arm (3, 103) is pivotally connected to the first vehicle mass (4, 104) around a pivot axis (P), to support the second vehicle mass (6, 106);

the spring means (5, 105) produce a spring force (F_s), exerting a counter moment (M_c) on the bearing arm (3, 103); and

the adjustment means (110) are arranged to vary said counter moment (M_c) by altering the direction of the spring force (F_s) and/or move its point of application (P_a) in a first direction, characterized in that the adjustment means (110) are furthermore arranged to move the point of application (P_a) of the spring force (F_s) in a second direction, in which the counter moment is not or hardly affected, but the effective spring stiffness (C_eff) of the suspension assembly (1, 101) is affected by the movement of the point of application (P_a), wherein the adjustment means (110) are further adapted to move the point of application (P_a) of the spring force (F_s) along a predetermined two dimensional path (QC), wherein a direction of a normal (M) of a plane accommodating said path includes an acute angle with both a direction (Y) of the pivot axis (P) and a direction (X) of the bearing arm (3, 103).

2. Suspension assembly (1, 101) according to claim 1, wherein the first direction is selected to cause a shortest distance (W) between the line of action of the spring force (F_s) and the pivot axis (P) to be increased or decreased, and wherein the second direction is selected to lie within a first plane (V₁), which extends perpendicular to the direction of said shortest distance (W) and contains the line of action of the spring force (F_s), and furthermore is selected to cause a distance (h) between the point of application (P_a) of the spring force (F_s) and a second plane through said shortest distance (W) and the pivot axis (P) to be increased or decreased in a predetermined way.

3. Suspension assembly (1, 101) according to claim 1, wherein the adjustment means (110) are arranged to move the point of application (P_a) of the spring force (F_s) along a predetermined path (Q, C), each point of said path (Q,C) representing a specific combination of a counter moment and a desired effective spring stiffness.

4. Suspension assembly (1, 101) according to claim 1, wherein the adjustment means (110) are arranged to move the point of application (P_a) of the spring force (F_s) along a predetermined linear path (Q).

5. Suspension assembly (1, 101) according to claim 1, wherein the adjustment means (110) are arranged to move the point of application (P_a) of the spring force (F_s) along a predetermined, two dimensional path (C).

6. Suspension assembly (101) according to claim 5, wherein the predetermined path is a circular path (C).

7. Suspension assembly (101) according to claim 6, wherein a centre line (M) of said circular path (C) includes an acute angle ( ) with a centre line (S) of the spring means (105).

8. Suspension assembly (101) according to claim 6, wherein a centre point of said circular path (C) is situated at a distance (Δ

y) from a centre point of the bearing arm (103) seen in Y-direction, extending parallel to the pivot axis (P).

9. Suspension assembly (1, 101) according to claim 1, wherein, under static load conditions, the point of application (P_a) of the spring force (F_a), is situated at a distance (Δ

z) above a plane defined by the pivot axis (P) and the bearing arm (3, 103).

10. Suspension assembly (1, 101) according to claim 1, wherein the adjustment means (110) are arranged to move the point of application (P_a) of the spring force (F_s) along a predetermined path (Q, C), causing the counter moment to vary between a minimum and a maximum value, while keeping the effective spring stiffness (C_eff) of the suspension assembly substantially constant.

11. Suspension assembly according to claim 1, wherein the adjustment means (110) are arranged to move the point of application (P_a) of the spring force (F_s) along a predetermined path (Q, C), causing the effective spring stiffness (C_eff) of the suspension assembly to increase with increased counter moment, so as to keep a natural frequency of the sprung second vehicle mass (6, 106) substantially constant.

12. Suspension assembly (1, 101) according to claim 1, wherein the spring force (F_a) is exerted on the bearing arm (3, 103) via an elongated member (108).

13. Suspension assembly (1, 101) according to claim 12, wherein the elongated member (108) is a string or a rod.

14. Suspension assembly (101) according to claim 12, wherein the elongated member (108) describes a cone during adjustment of the point of application (P_a).

15. Suspension assembly (101) according to claim 12, wherein the elongated member (108), under static load conditions, has its centre line aligned with the centre line (S) of the spring means (105).

16. Suspension assembly according to claim 12, wherein the elongated member (108), under static load conditions, extends substantially perpendicular to the bearing arm (103).

17. Suspension assembly (101) according to claim 12, wherein the spring means (105) comprise a guiding construction (107, 109, 113;

114, 115, 116) for guiding an end of the elongated member (108) within the spring means (105), so as to allow axial displacement of said end along a centre line (S) of the spring means (105).

18. Suspension assembly (1, 101), according to claim 1 wherein the spring means (5, 105) are pre-tensioned to produce a spring force (F_s), which may be a tensile force or a pressure force.

19. Suspension assembly (1, 101) according to claim 1, wherein the magnitude of the spring force (F_s) under static load conditions is adjustable.

20. Suspension assembly (1, 101) according to claim 1, wherein the counter moment, exerted on the bearing arm (3, 103) under static load conditions, is zero and an auxiliary spring is provided, to support the external load under said static load conditions.

21. Vehicle (2) comprising a chassis as the first vehicle mass (4, 104), a cabin or a wheel as the second vehicle mass, and an active suspension assembly (1, 101) according to claim 1, for suspending said second vehicle mass (6, 106) to the first vehicle mass (4, 104).

22. Active suspension assembly (1, 101) for use in a vehicle to suspend a second vehicle mass (6, 106) to a first vehicle mass (4, 104), the assembly (1, 101) comprising a bearing arm (3, 103), spring means (5, 105) and adjustment means (110), wherein in use:

the bearing arm (3, 103) is pivotally connected to the first vehicle mass (4, 104) around a pivot axis (P), to support the second vehicle mass (6, 106);

the spring means (5, 105) produce a spring force (F_s), exerting a counter moment (M_c) on the bearing arm (3, 103); and

the adjustment means (110) are arranged to vary said counter moment (M_c) by altering the direction of the spring force (F_s) and/or move its point of application (P_a) in a first direction, characterized in that the adjustment means (110) are furthermore arranged to move the point of application (P_a) of the spring force (F_s) in a second direction, in which the counter moment is not or hardly affected, but the effective spring stiffness (C_eff) of the suspension assembly (1, 101) is affected by the movement of the point of application (P_a), wherein the adjustment means (110) are arranged to move the point of application (P_a) of the spring force (F_s) along a predetermined, three dimensional (3D-) path.