DE102010020052A1 - Gas spring damper device, particularly for motor vehicle, has working piston provided with inlet of hydraulic device, in which hydraulic fluid flows when approaching working piston to stopper - Google Patents

Abstract

The gas spring damper device (1) has a working piston (7) provided with an inlet (47) of a hydraulic device (23), in which hydraulic fluid (13) flows when approaching the working piston to a stopper (41). The working piston lies along a path portion (43) of a spring damper displacement (45) at the stopper, where the stopper closes the inlet.

Description

The invention relates to a gas spring damper device, in particular for a motor vehicle, with a working cylinder, a displaceably mounted within the working cylinder along a spring damper and the working cylinder in a filled with a hydraulic medium or fillable first working space and a hydraulic medium filled or filled with the second working space dividing piston, a plunger rod fixedly assigned to the working piston and plunging into the first working space can be introduced into the gas spring damper device by means of plunging movement along the spring travel, and vice versa, a plucking point hydraulically associated with at least one of the working spaces and having a gas compensation space filled or filled with a compressible medium by means of at least a subset of the hydraulic energy introduced during the immersion movement, in particular by means of the compressible medium can be stored, and a hydraulic device which is connected between the first working space and the second working space and over which the hydraulic medium flows by converting a further subset of the hydraulic energy into heat energy during the submerged movement or a rebound movement between the working spaces.

Gas spring damper devices are known. They can be used for example as shock absorbers in motor vehicles. By means of the hydraulic device, a body movement of the motor vehicle can be damped, wherein during a dipping movement and a rebound movement in the gas spring damper device existing hydraulic energy can be converted into heat energy. Hydraulic energy can be understood as mechanical energy, in particular in the form of pressure energy. It is known to make the conversion into heat energy, ie the removal of the introduced hydraulic energy progressively, so that, for example, at the end of a spring travel, a higher level of energy can be withdrawn. The DE 28 06 541 A1 refers to a shock absorber or a strut with hydraulic-mechanical tension stop, a mounted on a piston rod and damping devices for the tensile and the pressure damping exhibiting piston is arranged axially movable in a cylinder and separates the cylinder interior into two fluid-filled work spaces and at one Cylinder end is a guide and a seal for the piston rod, while the hydraulic-mechanical Zuganschlag is disposed in the annular working space between the cylinder and piston rod and has a standing under the action of a spring damping ring and the piston rod is provided with a stop ring. There are provided an actuating ring and a stop for a spring. This results in a combination of hydraulic damping and a spring force counteracting a direction of movement. It is achieved a superposition of a speed-dependent hydraulic stop damping with a path-dependent acting spring force damping.

The object of the invention is to provide an improved gas spring damper device, in particular to allow an at least two-stage damper characteristic.

The object is in a gas spring damper device, in particular for a motor vehicle, with a working cylinder, a slidably mounted within the working cylinder along a Federdämpferwegs and the working cylinder in a filled or filled with a hydraulic medium first working space and a filled or filled with the hydraulic medium second working space working piston , a piston rod fixedly assigned and immersed in the first working space by means of the spring travel in a plunge hydraulic energy into the gas spring device is introduced, and vice versa, at least one of the working spaces hydraulically assigned and filled with a compressible medium or fillable gas compensation chamber Compliancy point by means of at least a subset of the recoverable during the immersion movement hydraulic energy convertible, in particular by means of de storable and is a connected between the first working space and the second working space hydraulic device over which the hydraulic medium under conversion of a further subset of the hydraulic energy in heat energy in the plunge movement or a rebound movement between the working spaces overflowed solved in that the working piston an inlet the hydraulic device, in which the hydraulic medium flows in an approach of the working piston to a stop, wherein the working piston along a partial path of the spring damper path abuts against the stop and the stop closes the inlet at least partially. Advantageously, the at least partially closed inlet acts as an additional hydraulic resistance, which is advantageously effective along the partial travel of the spring damper path. Advantageously, therefore, there is an increased attenuation along the partial path, so that there is advantageously at least a two-stage damping characteristic of the gas spring damper device, whereby as long as the inlet is fully open, a weaker damping is established than during the partial path along which the stop is connected as an additional series hydraulic resistance acts.

In one embodiment of the gas spring damper device, it is provided that a spring introduced into one of the working spaces, in particular annular spring and / or plate spring, has the stop. Advantageously, it can be ensured in a simple manner by means of the spring force that the stop bears against the working piston along the partial path, that is to say advantageously the inlet is at least partially closed more securely.

In a further embodiment of the gas spring damper device is provided that the working piston and the spring rest in a positive contact contact with each other. Advantageously, an exact relative positioning of the working piston and the spring to each other take place by means of the positive contact contact, wherein it is ensured that even with a variety of immersion movements and opposite rebound movements each an exactly constant partial closure of the inlet and thus adjusting the additional hydraulic resistance.

In a further embodiment of the gas spring damper device is provided that a spring assembly of the hydraulic device is immersed during the contact contact in a circular space of the spring. The hydraulic device may comprise a so-called spring assembly, by means of which an overflow between the working chambers on the plunging movement and the rebound movement is adjustable or adjusted. This spring assembly is assigned to the working piston centered and can advantageously dip into the annular space of the spring, so that the spring present in the working space advantageously does not limit the Federdämpferweg.

In a further embodiment of the gas spring damper device is provided that the second working space of the gas spring damper device comprises the stop. The second working space may constitute a so-called pressure area of the gas spring damper device, that is to say an area which is pressurized during the dipping movement. Advantageously, the immersion movement can be progressively damped, wherein during the approach of the working piston to the stop a first, weaker damping and during the abutment of the stop on the working piston is given a further higher damping. Advantageously, the damping can be reinforced at one end of the spring damper path.

In a further embodiment of the gas spring damper device is provided that the first working space of the gas spring damper device comprises the stop. The first working space can make a so-called train area, which is pressurized during the rebound movement. Advantageously, a, in particular forced, rebound movement can thereby be progressively damped.

In a further embodiment of the gas spring damper device, it is provided that the first working space and the second working space each have a stop and an associated inlet. Advantageously, the pressure range and the tension range can equally be progressively damped.

The object is also achieved in a motor vehicle with a gas spring damper device described above. This results in the advantages described above.

Further advantages, features and details will become apparent from the following description in which - where appropriate, with reference to the drawings - at least one embodiment is described in detail. Described and / or illustrated features form the subject of the invention, or independently of the claims, either alone or in any meaningful combination, and in particular may additionally be the subject of one or more separate applications. The same, similar and / or functionally identical parts are provided with the same reference numerals. Show it:

1 a gas spring damper device with a ring spring having a stop, wherein a dipping motion is symbolized by means of arrows;

2 in the 1 shown gas spring damper device, wherein in contrast by means of arrows a rebound movement is symbolized;

3 in the 1 and 2 shown gas spring damper device in the region of a partial path at the end of a Federdämpferwegs; and

4 another gas spring damper device analogous to that in the 1 and 3 represented, by means of arrows a rebound movement is shown, in contrast, two ring springs are provided.

1 shows a gas spring damper device 1 , the part of a motor vehicle only partially shown 3 is. The gas spring damper device 1 has a working cylinder 5 on. Inside the working cylinder 5 is a working piston 7 mounted longitudinally displaceable. The working piston 7 separates the working cylinder 5 in a first workroom 9 and a second workspace 11 , The workrooms 9 . 11 are with a hydraulic medium 13 filled, for example, a hydraulic oil. Furthermore, within the working cylinder 5 a compliance point 15 arranged, which has a separating piston and a filled with a compressible medium gas compensation chamber 19 having. For the compressible medium of the gas equalization chamber 19 For example, it can be air or any other gas. The separating piston 17 separates the hydraulic medium 13 from the gas compensation room 19 and is also longitudinally displaceable within the working cylinder 5 stored. The gas spring damper device 1 works by means of the working piston 7 , the separating piston 17 and the gas compensation room 19 after the so-called Einrohrdämpferprinzip, which is known and will not be explained in detail here.

The working piston 7 is a piston rod 21 assigned to the fluid-tight against the working cylinder 5 is sealed and stands out from this. By means of the piston rod 21 can apply mechanical energy to the working piston 7 be transferred, this mechanical energy is converted into hydraulic energy, in particular in the form of pressure energy of the gas in the compensation chamber 19 located compressible medium. During a dipping movement or a rebound movement of the working piston 7 or the associated piston rod 21 the hydraulic medium flows 13 between the workrooms 9 and 11 above. For this purpose, the working piston 7 a hydraulic device 23 with an upper spring package 25 and a lower spring package 27 on. The upper spring package 25 is within the first workspace 9 arranged.

The lower spring package 27 is within the second workspace 11 arranged. The spring packages 25 . 27 each have so-called spring washers and provide a hydraulic resistance for the between the work spaces 9 and 11 overflowing hydraulic medium 13 ready.

The working piston 7 has a fluid path 29 For example, a hole on. By means of a first arrow 33 is a volume flow of the hydraulic medium 13 from the second workspace 11 in the first workroom 9 through the fluid path 29 symbolized through. By means of a second arrow 35 is a plunging motion of the working piston 7 symbolizes. By means of a third arrow 37 is a corresponding displacement of the separating piston 17 symbolizes.

2 shows the in 1 shown gas spring damper device, wherein, in contrast, the working piston 7 performs a rebound movement, which by means of the second arrow 35 is symbolized. It can be seen that it also moves the separating piston in the opposite direction, which means the third arrow 37 is shown. Another difference is by means of the upper spring package 25 the fluid path 29 locked. Instead, by means of the lower spring package 27 another fluid path 31 , For example, a bore, the working piston 7 opened, allowing a flow of air from the first working space 9 in the second working space through the further fluid path 31 what can flow in 2 by means of the first arrow 33 is symbolized.

3 shows the in the 1 and 2 shown gas spring damper device 1 analogous to the representation of 1 , that is, during an immersion movement, in contrast to the piston rod 21 almost completely submerged, the working piston 7 is located in the area of a lower end position. It can be seen that there is a spring 39 in the second workroom 11 is introduced, in abutting contact with the working piston 7 located. The feather 39 has an annular stop 41 on, on which the working piston 7 along a partial route 43 a spring damper path 45 is applied.

It can be seen that the annular stop 41 the feather 39 , which is designed for example as a ring spring, an inlet 47 of the fluid path 29 at least partially closes. This forms the stop 41 the feather 39 along with the inlet 47 a hydraulic resistance, in addition to another hydraulic resistance coming from the upper spring package 25 is formed, connected in series. Advantageously finds an overflow of the second working space 11 in the first workroom 9 along the partial route 43 of the spring damper route 45 in the submerged motion under a higher hydraulic resistance. Advantageous is the partial route 43 at one end of the suspension damper path 45 , so that with a nearly complete immersion movement a higher damping is available.

4 shows another gas spring damper device 1 analogous to the gas spring damper device shown in the previous figures 1 , In the following, only the differences are discussed.

In contrast to the representation of the 1 to 3 has the gas spring damper device 1 according to 4 another spring 49 on that within the first workspace 9 is arranged. The other spring 49 indicates another stop 51 on, on which the working piston 7 at the end of a rebound movement strikes. There is another inlet 53 the further fluid path 31 at least partially closed, whereby advantageously analogous to the representation of 3 also in the rebound movement a series-connected additional hydraulic resistance to a hydraulic resistance of the lower spring assembly 27 established. Advantageously, the rebound movement can be progressive or multi-stage, in particular two-stage, damped.

Advantageously, by the spring 39 and / or the other spring 49 additional, path-dependent, series-connected hydraulic resistances or flow resistances are generated, wherein the gas spring damper device 1 is constructed according to the classic Einrohrdämpferprinzip. These additional flow resistances can advantageously from a defined Einfahrweg or Federdämpferweg the piston rod 21 , according to the 1 to 3 in a pressure range and according to the 4 also be activated in a train area. Advantageously, strong deflections, as for example in driving safety relevant extreme maneuvers of the motor vehicle 3 occur additionally hydraulically attenuated. Advantageously, this opens up the possibility of a non-illustrated suspension of the motor vehicle 3 for a normal driving range, as in the 1 and 2 without compromise in the light of the existence of extreme maneuvers. A tuning scope that advantageously offers this can be advantageously used in favor of a comfort-oriented suspension design. The path-dependent, series-connected flow resistance of the partially closed inlet 47 or further inlet 53 can be activated if the piston rod 21 reaches a defined retraction position, ie the partial path 43 reached. In this position, the working piston hits 7 on the relaxed spring 39 , which can be designed in particular as a spiral or plate spring. The feather 39 is from an inner diameter of the working cylinder 5 guided and by the separating piston 17 supported, with which it is firmly connected.

Through the contact between the working piston 7 or a piston valve and the spring 39 creates a contact, in particular a positive connection. Through this investment contact, in particular the positive connection, is a cross section of the inlet 47 of the fluid path 29 or a pre-restrictor of the piston valve narrows. This cross-sectional constriction of the choke or the inlet 47 leads advantageously to a higher flow resistance and thus in the last consequence to a higher damping force in the pressure range, ie during the in 3 shown immersion movement along the part way 43 of the spring damper route 45 ,

The strength of the increase in the flow resistance as a result of the contact, in particular the positive connection, between the working piston 7 and the spring 39 can readily by reducing an inner diameter of the spring 39 be scaled. This reduction in the inner diameter of the spring 39 leads to a larger coverage of the opening cross-section of the inlet 47 and thus to a higher flow resistance for the hydraulic medium 13 in the working cylinder 5 ,

It is advantageous kinematically an additional retraction of the piston rod 21 in the working cylinder 5 along the partial route 43 of the spring damper route 45 even after the contact or during the contact between the working piston 7 and the spring 39 readily possible because the Zugdämpfungsrelevante lower spring package 27 in an annular space of the spring 39 can dive.

A spring force effect of the spring 39 on the working piston 7 or by means of the working piston 7 on the piston rod 21 can by a corresponding design of the spring 39 be scaled arbitrarily.

A tensile damping force of the gas spring damper device 1 is due to the contact of the working piston 7 at the spring 39 not affected or impaired.

Moves the piston rod 21 inside the working cylinder 5 in the in 2 shown direction, which leads to an increasing relaxation of the spring 39 leads, this ultimately happens a position that the relaxed spring 39 corresponds, wherein advantageously the partially closed inlet of the fluid path 29 , so a Vorordel of the working piston 7 is released again. This is the case when the partial route 43 in the in 2 shown direction, ie during a rebound movement, completely traversed. Releasing the opening cross-section of the inlet 47 means a lower flow resistance for the hydraulic medium 13 in the pressure range and thus ultimately lower damping forces the pressure level above a position of the piston rod 21 giving a relaxed length of the spring 39 equivalent.

Close to a KO situation, the gas spring damper device designed as a one-pipe pressure step damper behaves 1 in terms of a compression damping like a conventional mono-tube damper. Under a KO position can be a rest position of the motor vehicle 3 be understood at a defined loading.

In the normal situation, there are advantageously no restrictions with regard to acoustics or driving comfort of the motor vehicle 3 ,

In addition, the gas spring damper device behaves 1 near the KO position also with respect to a rebound damping, as in 2 is shown as a conventional monotube. Advantageously, there are no restrictions with regard to the acoustics or the driving comfort.

In case of very strong deflection, as in 3 is shown, is advantageously a progressive damping behavior of Gas spring damper device 1 due to the at least partially closed inlet 47 of the fluid path 29 given. Advantageously, thereby the compression damping can be significantly increased. This increase in the flow resistance is achieved by the application of the piston valve or the working piston 7 and thus the intake 47 to the stop 41 the feather 39 , Due to the restoring force of the spring 39 this contact remains along the partial route 43 of the spring damper route 45 receive. Alternatively and / or additionally, a positive connection for an exact relative positioning of the spring 39 to the working piston 7 be provided.

For extreme maneuvers, for example a so-called Fishhook maneuver, this advantageously provides an additional damping force potential, which can lead to the existence of such maneuvers, wherein advantageously no comfort restrictions have to be accepted in a normal driving range.

The spring is advantageous 39 firmly with the separating piston 17 connected, so that these of the piston valve or the working piston 7 in the event of a return to the KO situation, ie during the rebellious movement, without further ado from the pen 39 solves. Thus, even after an extreme compression, as in 3 Again, a comfort-oriented compression damping of the KO position is available.

Alternatively and / or additionally, it is possible, as in 4 shown, the rebound damping, designed in two stages with a very strong rebound analog of the compression damping.

LIST OF REFERENCE NUMBERS

1

Gas spring damper device

3

motor vehicle

5

working cylinder

7

working piston

9

first working space

11

second workspace

13

hydraulic medium

15

compliance point

17

separating piston

19

Gas compensation space

21

piston rod

23

hydraulic device

25

Upper spring package

27

lower spring package

29

fluid path

31

fluid path

33

first arrow

35

second arrow

37

third arrow

39

feather

41

attack

43

partial route

45

Federdämpferweg

47

inlet

49

feather

51

attack

53

inlet

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 2806541 A1 [0002]

Claims (8)

Gas spring damper device ( 1 ), in particular for a motor vehicle ( 3 ), with: - a working cylinder ( 5 ), - one within the working cylinder ( 5 ) along a spring damper path ( 45 ) displaceably mounted and the working cylinder ( 5 ) in a filled with a hydraulic medium or fillable first working space ( 9 ) and a filled with the hydraulic medium or fillable second working space ( 11 ) dividing working piston ( 7 ), - one of the working piston ( 7 ) and into the first workspace ( 9 ) submerged piston rod ( 21 ) by means of along the spring damper path ( 45 ) in a plunge motion hydraulic energy into the gas spring damper device ( 1 ) and vice versa, - at least one of the workspaces ( 9 . 11 ) hydraulically associated and filled with a compressible medium or fillable gas compensation chamber ( 19 ) (3) 15 ) can be converted by means of the at least one subset of the hydraulic energy that can be introduced during the immersion movement, in particular by means of the compressible medium, is storable, one between the first working space ( 9 ) and the second workspace ( 11 ) connected hydraulic device ( 23 ) via which the hydraulic medium ( 13 ) by converting a further subset of the hydraulic energy into heat energy during the immersion movement or a rebound movement between the work spaces ( 9 . 11 ), characterized in that the working piston ( 7 ) an inlet ( 47 ) of the hydraulic device ( 23 ) into which the hydraulic medium ( 13 ) at an approach of the working piston ( 7 ) to a stop ( 41 ), wherein the working piston ( 7 ) along a partial route ( 43 ) of the spring damper path ( 45 ) at the stop ( 41 ) and the attack ( 41 ) while the inlet ( 47 ) at least partially closes. Gas spring damper device according to the preceding claim, characterized in that one in one of the working spaces ( 9 . 11 ) introduced spring ( 39 ), in particular an annular spring and / or a plate spring, the stop ( 41 ) having. Gas spring damper device according to the preceding claim, characterized in that the working piston ( 7 ) and the spring ( 39 ) abut each other in a positive contact with each other. Gas spring damper device according to the preceding claim, characterized in that a spring assembly ( 25 . 27 ) of the hydraulic device ( 23 ) during the abutment contact in an annular space of the spring ( 39 ) is immersed. Gas spring damper device according to one of the preceding claims, characterized in that the second working space ( 11 ) of the gas spring damper device ( 1 ) the attack ( 41 ) having. Gas spring damper device according to one of the preceding claims, characterized in that the first working space ( 9 ) of the gas spring damper device ( 1 ) another stop ( 51 ) having. Gas spring damper device according to one of the preceding claims, characterized in that the first working space ( 9 ) and the second workspace ( 11 ) the attack ( 41 ) and the further stop ( 51 ), the stop ( 41 ) with the inlet ( 47 ) and the further stop ( 51 ) with another inlet ( 53 ) of the working piston ( 7 ) cooperates. Motor vehicle ( 3 ) with a gas spring damper device ( 1 ) according to any one of the preceding claims.

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