A fluid spring

Abstract: According to an illustrative example a gas spring comprises a cylinder (10) and a piston rod (11) axially movable with respect to the cylinder. The piston rod is guided through a guiding and sealing ring (13) adjacent one end of the cylinder. A piston (12) is fastened within the cylinder with the inner end of the piston rod. The piston is provided with an axial passage (20) connecting the two working chambers on both sides of the piston. A pressurized gas is provided within both working chambers. One of the working chambers is connected with a pressure reservoir (2). The pressure of gas within the pressure reservoir is larger than the pressure within the working chambers. A shut-off valve (5) is pro­ vided between the pressure reservoir and the respective working chamber. This shut-off valve is automatically controlled such as to admit pressurized gas from the reservoir to the respective chamber when the pressure value within the respective working chamber falls below a predetermined pressure value. The shut-off valve is closed again when the pressure within the respective working chamber has risen again up to a determined pressure value. Such it is warranted that the pressure within the working chambers does not fall below the predetermined value as long as the increased pressure within the reservoir exists.

Description: BACKGROUND OF THE INVENTION The invention relates to a fluid spring. The spring action of such a fluid spring should remain nearly constant over a long period of operation. However, it occurs sometimes that pressurized fluid escapes through the sealing means through which the piston rod passes. In order to nevertheless maintain a nearly constant pressure within the cylinder, compensating means are provided which allow a correction of the pressure acting on the piston rod. STATEMENT OF THE PRIOR ART A gas spring which comprises a pressure reservoir connectable with the working chamber through a shut-off valve is known from German Patent 1,282,364. To vary the outward thrust force of the piston rod the shut-off valve is opened by the piston rod when the piston rod is fully pushed inwards, so that the connection of the working chamber with the pressure reservoir having a higher gas pressure is effected by such valve actuation. The valve actuation is dependent upon the piston rod stroke. It is disadvantageous that such a pressure correction in the working chamber cannot be effected in a sufficiently sensitive manner and it is further disadvantageous that the correction of pressure can be effected only in a definite position of the piston rod which must be achieved by an external force acting on the piston rod. From US-A-4 662 616 there is further known a gas spring comprising a container and a plunger movable with respect to the container. A gas chamber is defined within the container. This gas chamber contains a volume of a pressurized gas. This volume of pressurized gas serves a force onto the plunger. The gas chamber is in a flow connection with a reservoir of pressurized gas outside the gas spring. The pressure of the pressurized gas is larger than the pressure within the gas chamber. A valve is provided in the gas flow connection between the gas chamber and the reservoir. The valve comprises a valve member. This valve member opens and closes the glas flow connection in response to its respective position. The position of the valve member is responsive to a control signal provided by the action of a resilient means and to the actual pressure within the gas chamber. In addition to the action of the resilient means and to the action of the actual pressure within the gas chamber, the valve member is also exposed to the pressure within the pressure reservoir. As a result of this influence of the pressure in the pressure reservoir, the control function of the valve member is dependent on the pressure within the pressure reservoir. A control of the gas pressure within the gas chamber of the gas spring is only possible when the pressure within the pressure reservoir is always kept precisely constant. This can be done by providing a further control system stabilizing the pressure within the pressure reservoir. This requires, however, a complicated and expensive control system. Gas springs particularly in motor vehicles and in chair constructions are frequently independent of external fluid supply. Therefore, it is not possible with the known device to maintain a substantially constant pressure within the gas chamber. OBJECT OF THE INVENTION It is the object of the invention to provide a fluid spring in which the pressure of the pressurized fluid chamber can be automatically corrected independent of the respective position of the piston rod. A further object of the invention is to provide correction means which allow a very sensitive correction of the pressure of the pressurized fluid. The present invention relates to a fluid spring comprising a container and a plunger member movable with respect to said container, at least one fluid chamber being defined within said container, said at least one fluid chamber containing a volume of pressurized fluid, said volume of pressurized fluid exerting a force onto said plunger member, said at least one fluid chamber being in fluid flow connection with a reservoir of pressurized fluid, the pressure of pressurized fluid within said reservoir being larger than the pressure of pressurized fluid within said at least one fluid chamber, shut-off valve means being in said fluid flow connection between said at least one fluid chamber and said reservoir, said shut-off valve means comprising a valve member, said valve member opening and closing said fluid flow connection in response to its position, the position of said valve member being responsive to a control signal provided by the action of resilient means and to a further control signal provided by the actual pressure within said at least one fluid chamber. In view of the above object of the invention it is proposed that said valve member is loaded in opposite directions by the actual pressure within said at least one fluid chamber and said resilient means and is substantially free from loading action of said pressure within said reservoir, such that said shut-off valve is opened when the actual value of pressure within said at least one fluid chamber falls below a first predetermined value represented by said resilient means and is closed when said actual value of pressure within said at least one fluid chamber approaches said first predetermined pressure value. By this design of the fluid spring it is achieved that the pressure within the fluid chamber cannot fall below the first predetermined pressure value as long as the increased pressure within the pressure reservoir exists. Such a nearly constant thrust force on the plunger is guaranteed over a long period of operation. No external influence must be exerted in order to maintain the substantially constant pressure and the substantially constant force acting on the plunger member. According to a further development of the invention the fluid chamber is connected with atmosphere through a further shut-off valve. This further shut-off valve is controlled by a still further control signal representing a second predetermined pressure value of the pressure within the fluid chamber and by a still further control signal representing the actual value of pressure within the fluid chamber. This further shut-off valve is opened when the actual value of pressure within the fluid chamber raises beyond the second predetermined value of pressure. It is closed again when the actual value of pressure within the fluid chamber approaches the second predetermined pressure value. By this further development it is achieved that the pressure within the fluid chamber cannot rise beyond the second predetermined value of pressure. It is evident that the constancy of the pressure within the fluid chamber is at an optimum if the second predetermined pressure value is close to the first predetermined pressure value. If the pressure within the fluid chamber is substantially independent of the relative position of the container and the plunger member, the second predetermined value of pressure may be substantially equal to the first predetermined value of pressure. In most cases it is sufficient if the pressure within the fluid chamber is maintained within a predetermined range of pressure values. Such, thesecond predetermined value of pressure may be larger than the first predetermined value of pressure. With such a design, the shut-off valve and - as the case may be - the further shut-off valve - are opened only when the limits of the range are exceeded. So there is no risk that the pressurized fluid in the pressure reservoir is exhausted too early. If the actual pressure within the fluid chamber is dependent on the position of the plunger member with respect to the container, and if the plunger member is movable between two terminal positions with respect to the container, the movement of the plunger member between the two terminal positons results in a difference of the actual values of pressure. In this case the difference of the second predetermined value of pressure and the first predetermined value of pressure should be at least equal to the above-mentioned difference of actual values of pressure. By this condition it is guaranteed that the correction of the pressure within the fluid chamber is suppressed as long as only pressure variations occur in response to the movement of the plunger between its terminal positions. Such a too early exhaustof the pressure reservoir is again avoided. The control signal provided by the action of said resilient means representing the first predetermined pressure value may be adjustable, and also the still further control signal representing the second predetermined pressure value may be adjustable. An analogous design may be used for the further shut-off valve as for said shut-off valve. The pressure reservoir and the shut-off valve may be integrated with the fluid spring, such that a very compact unit is obtained, e.g. the pressure reservoir and the shut-off valve may be integrated with the container of the fluid spring or alternatively with the plunger member. It is however also possible that the fluid spring and the reservoir are separated from each other and are interconnected by an external fluid flow connection line. The fluid spring may be a gas spring in which case the pressurized fluid within the container comprises a volume of pressurized gas. The pressure within the reservoir may be maintained in that the pressurized fluid within the reservoir comprises also a volume of pressurized gas. According to a preferred embodiment both the container and the reservoir contain a volume of pressurized gas, and these volumes of pressurized gas are interconnected by the fluid flow connection. The fluid spring may be designed in the style of a conventional gas spring; in such case the container is a cylinder having an axis and two ends and defining a cavity therein. A piston rod guiding and sealing unit is provided adjacent one of the two ends. The plunger member is a piston rod member extending inwards and outwards of the cavity. A piston unit is connected with the piston rod member within the cavity. The piston unit separates the cavity into two working chambers. The working chambers are interconnected across the piston unit. Both working chambers contain a pressurized fluid. The pressurized fluid in at least one of the working chambers comprises a volume of pressurized gas. The various features of novelty which characterize the invention are pointed out with particularity in the claims annexed to and forming a part of this disclosure. For a better understanding of the invention, its operating advantages and specific objects attained by its use, reference should be had to the accompanying drawings and descriptive matter in which there are illustrated and described preferred embodiments of the invention. BRIEF DESCRIPTION OF THE DRAWINGS The invention will be explained in greater detail hereinafter with reference to the embodiments shown in the accompanying drawings in which: FIGURE 1 shows a gas spring with a reservoir integrated within the container; FIGURE 2 shows an embodiment in which the reservoir is integrated within the plunger; FIGURE 3 shows an embodiment in which the reservoir is bodily separated from the container and is connected with the container through a connection line; FIGURE 4 shows an embodiment corresponding to FIGURE 3 in which the container is connectable with atmosphere through a further shut-off valve and FIGURE 5 shows by way of example a valve unit to be used as said shut-off valve or as said further shut-off valve. DESCRIPTION OF THE PREFERRED EMBODIMENTS The gas spring according to Figure 1 possesses a cylinder 10 in which there slides a piston 12 connected with a piston rod 11. A piston rod guiding and sealing unit 13 is provided at the upper end of the cylinder 10 and seals off to the exterior. A cavity 1 is situated in the interior of the cylinder 10. This working chamber 1 possesses a gas filling under pressure, whereby the piston rod 11 is subject to an outward thrust force. The outward thrust force here corresponds to the product of the pressure in the cavity 1 and the cross-sectional area of the piston rod 11. Likewise in the cylinder 10 a pressure reservoir 2 is provided adjoining the cavity 1 and is connectable with the cavity 1 by way of a pressure-dependently acting valve 5. There is a higher gas pressure in the pressure reservoir 2 than in the cavity 1, so that when the pressure reservoir 2 is connected with the cavity 1 through the pressure-dependently acting valve 5, gas flows out of the pressure reservoir 2 into the cavity 1. The pressure-dependently acting valve 5 comprises a valve body which is loaded for the one part, through a control conduit 3 connected with the cavity 1, by the pressure in the cavity 1 and for the other part by a spring element 4. By means of the pre-stress of the spring element 4 the pressure-dependently acting valve 5 can be adjusted to a predetermined pressure to be maintained in the cavity 1. If the actual pressure in the cavity 1 falls below the predetermined pressure, the displacement of the valve body by the spring element 4 has the effect that the pressure reservoir 2 is connected with the cavity 1 until the predetermined pressure is reached again in the cavity 1 and the pressure-dependently acting valve 5 closes the connection again. Thus by means of the pressure-dependently acting valve 5 the pressure in the cavity 1 and thus the outward thrust force of the piston rod 11 can be kept constant, at least as long as a higher pressure prevails in the pressure reservoir 2 than in the cavity 1. Slight pressure losses in the cavity 1, which occur for example due to escape of gas by way of the piston rod sealing and guiding unit 13, can thus be readily compensated. The pressure-dependently acting valve 5 thus operates in dependence on the actual pressure in the cavity 1. The connection between the reservoir 2 and the cavity 1 is generally opened when the piston 12 and the piston rod 11 are in their outermost position as shown in Fig. 1 because the pressure in the cavity 1 falls when the piston rod 11 moves outwards due to increasing volume within the cavity 1. The form of embodiment according to Figure 2 differs from that according to Figure 1 essentially in that the pressure reservoir 2 is arranged in the piston rod 11. The pressure-dependently acting valve 5 is likewise provided in the piston rod 11, which valve is arranged in the connecting conduit between the pressure reservoir 2 and the cavity 1 and is loaded for the one part by the control conduit 3 and for the other by the spring element 4. If the pressure in the cavity 1 falls below the predetermined pressure, the pressure-dependently acting valve 5 opens, so that gas can flow out of the pressure reservoir 2 into the cavity 1 until the predetermined internal pressure is restored. When the predetermined pressure is reached in the cavity 1, the pressure-dependently acting valve 5 closes the connection to the pressure reservoir 2. The fluid flow connection containing the valve 5 is designated by 6 both in Figure 1 and 2. It is further to be noted that both in Figure 1 and 2 the piston 12 is provided with a bore 20 interconnecting respective working chambers on both sides of the piston 12. In the form of embodiment according to Figure 3 the pressure reservoir 2 is arranged outside the gas spring, that is outside the cylinder 10 and outside the piston rod 11. The cavity 1 situated in the cylinder 10 is in communication through a connecting conduit 6 and the pressure-dependently acting valve 5 with the pressure reservoir 2, with the pressure in the cavity 1 acting through the control conduit 3 upon the pressure dependently acting valve 5 and for the other part the pre-stressed spring element 4 serving for the exact setting of the pre-determined internal pressure in the cavity 1. In order to achieve a constant outward thrust force of the piston rod 11 especially even in such installation situations where the gas spring is subjected to great temperature fluctuations, in the example of embodiment according to Figure 4 a further pressure-limiting valve 7 is provided which is connected to the cavity 1. Thus in this example of embodiment the gas quantity replenished from the pressure reservoir 2 into the cavity 1 as a result of temperature drop can flow away to atmosphere through the pressure-limiting valve 7 if the temperature rises again, so that the same outward thrust force is always exerted upon the piston rod 11. The pressure-limiting valve 7 corresponds in construction to the pressure-dependently acting valve 5, that is here again an adjustable spring element is provided which constitutes the connection to atmosphere on exceeding the predetermined pressure in the cavity 1. It is readily possible to provide the pressure reservoir 2 with a filling valve 21 so that a simple replenishment of the pressure reservoir 2 is possible. The design according to the invention is suitable especially in the case of small gas spring dimensions in which the cavity 1 is likewise small such that slight gas losses would have a serious effect upon the outward force of the piston rod 11. In Figure 5 there is shown the pressure-dependently acting valve 5 in more detail. This valve comprises a valve cylinder 5a and a valve member 5b. The spring element 4 acts on the one side of the valve member 5b. The spring element 4 is supported by a wall member 5c which is again supported by an adjustable spindle 5d. The other side of the valve member 5b is subject to the pressure within the cavity 1 through line 3. The valve member 5b is to selectively close or shut-off the line 6 which extends from the pressure reservoir 2 to the cavity 1. The predetermined pressure value to be maintained within the cavity 1 is adjusted by adjustment of the spindle 5d which spindle is responsible for the pre-stress of the spring element 4. As long as the predetermined pressure value exists within the cavity 1, the line 6 is shut off. If the actual value within the cavity 1 falls below the predetermined value, the bore 23 within the valve member 5b enters into alignment with the line 6 so that pressurized gas flows from the pressure reservoir 2 into the cavity 1. So the actual value of pressure within the cavity 1 is increased again and the valve member 5b is moved to the left again in Figure 5 so that the line 6 is shut off again. The embodiment of the valve 7 in Figure 4 may be identical with the valve 5 as shown in Figure 5. However, the valve 5 and 7 in the case of Figure 4 are adjusted to different predetermined values. In such case the operation in Figure 4 is as follows: if the actual pressure within the cavity 1 is close above the predetermined pressure value of the valve 5 and the piston rod 11 is moved to the left, the actual pressure value within the cavity 1 is reduced below the predetermined value of pressure as defined by the valve 5. So the valve 5 is opened and additional gas under pressure enters into the cavity 1 until the actual value of pressure within the cavity 1 increases again up to the predetermined value defined by the valve 5. When the piston rod 11 is hereupon moved to the right again in Figure 4, the pressure within the cavity 1 is increased again. The predetermined value defined by the valve 7 is however such that the piston rod 11 can be moved to the right in Figure 4 until the piston 12 abuts the right hand end of the cylinder 10 without the predetermined pressure value defined by the valve 7 being reached. Only when an additional increase of the pressure within the cavity 1 occurs, e.g. by raising temperature, the predetermined value of valve 7 is reached and in this case the valve 7 opens and a part of the pressurized gas of the cavity 1 can escape to atmosphere, so the pressure within the cavity 1 is maintained continuously between the lower predetermined pressure defined by the valve 5 and the higher predetermined pressure as defined by the valve 7. Preferably, the difference between the lower predetermined pressure value as defined by the valve 5 and the higher predetermined pressure value as defined by the valve 7 is at least equal to the pressure difference resulting from the movement of the piston rod 11 between its outermost left position in Figure 4 and its innermost right position in Figure 4. While specific embodiments of the invention have been shown and described in detail to illustrate the application of the inventive principles, it will be understood that the invention may be embodied otherwise without departing from such principles. The reference numerals in the claims are only used for facilitating the understanding and are by no means restrictive.

Claims: A fluid spring comprising a container (10) and a plunger member (11) movable with respect to said container (10), at least one fluid chamber (1) being defined within said container (10), said at least one fluid chamber (1) containing a volume of pressurized fluid, said volume of pressurized fluid exerting a force onto said plunger member (11), said at least one fluid chamber (1) being in fluid flow connection with a reservoir (2) of pressurized fluid, the pressure of pressurized fluid within said reservoir (2) being larger than the pressure of pressurized fluid within said at least one fluid chamber (1), shut-off valve means (3, 5) in said fluid flow connection (6) between said at least one fluid chamber (1) and said reservoir (2), said shut-off valve means (3, 5) comprising a valve member (5b), said valve member (5b) opening and closing said fluid flow connection (6) in response to its position, the position of said valve member (5b) being responsive to a control signal provided by the action of resilient means (4) and to a further control signal provided by the actual pressure within said at least one fluid chamber (1), characterized in that said valve member (5b) is loaded in opposite directions by the actual pressure within said at least one fluid chamber (1) and said resilient means (4) and is substantially free from loading action of said pressure within said reservoir (2), such that said shut-off valve (5) is opened when the actual value of pressure within said at least one fluid chamber (1) falls below a first predetermined value represented by said resilient means and is closed when said actual value of pressure within said at least one fluid chamber (1) approaches said first predetermined pressure value. A fluid spring as set forth in claim 1, said at least one fluid chamber (1) being connected with atmosphere through a further shut-off valve (7), said further shut-off valve (7) being controlled by a still further control signal representing a second predetermined pressure value of said pressure within said at least one fluid chamber (1) and by a yet still further control signal representing the actual value of pressure within said at least one fluid chamber (1), said further shut-off valve (7) being opened when said actual value of pressure within said at least one fluid chamber (1) rises beyond said second predetermined value of pressure and being closed again when said actual value of pressure within said at least one fluid chamber (1) approaches said second predetermined pressure value. A fluid spring as set forth in claim 2, said second predetermined value of pressure being substantially equal to said first predetermined value of pressure. A fluid spring as set forth in claim 2, said second predetermined value of pressure being larger than said first predetermined value of pressure. A fluid spring as set forth in claim 4, said actual pressure within said at least one fluid chamber (1) being dependent on the position of said plunger member (11) with respect to said container (10), said plunger member (11) being movable between two terminal positions with respect to said container (10), movement of said plunger member (11) between said two terminal positions resulting in a difference of the actual values of pressure, the difference of said second predetermined value of pressure and said first predetermined value of pressure being at least equal to said difference of actual values of pressure. A fluid spring as set forth in one of claims 1 to 5, said control signal (4) provided by the action of said resilient means (4) representing said first predetermined pressure value being adjustable. A fluid spring as set forth in one of claims 2 to 6, said still further signal representing said second predetermined pressure value being adjustable. A fluid spring as set forth in one of claims 2 to 7, said further shut-off valve (7) comprising a valve member, said valve member opening and closing said at least one fluid chamber (1) with respect to atmosphere in response to its position, said valve member being subject to the action of a resilient means on the one hand and to the actual pressure within said at least one fluid chamber (1) on the other hand, the spring force of the said resilient means providing said still further signal representing said second predetermined pressure value. A fluid spring as set forth in one of claims 1 to 8 said pressure reservoir (2) and said shut-off valve (5) being integrated with said fluid spring. A fluid spring as set forth in claim 9, said pressure reservoir (2) and said shut-off valve (5) being integrated with said container (10) of said fluid spring. A fluid spring as set forth in claim 9, said pressure reservoir (2) and said shut-off valve (5) being integrated with said plunger member (11). A fluid spring as set forth in one of claims 1 to 8, said fluid spring and said reservoir (2) being separated from each other and being interconnected by an external fluid flow connection line (6). A fluid spring as set forth in one of claims 1 to 12, said pressurized fluid within said container (10) comprising a volume of pressurized gas. A fluid spring as set forth in one of claims 1 to 13, said pressurized fluid within said reservoir (2) comprising a volume of pressurized gas. A fluid spring as set forth in one of claims 1 to 12, both said container (10) and said reservoir (2) containing a volume of pressurized gas, said volumes of pressurized gas being interconnected by said fluid flow connection (6). A fluid spring as set forth in one of claims 1 to 15, said container (10) being a cylinder having an axis and two ends and defining a cavity (1) therein, a piston rod guiding and sealing unit (13) being provided adjacent one of said ends, said plunger member (11) being a piston rod member extending inwards and outwards of said cavity (1), a piston unit (12) being connected with said piston rod member (11) within said cavity (1), said piston unit (12) separating said cavity (1) into two working chambers, said working chambers being interconnected across said piston unit (12), both said working chambers containing a pressurized fluid, the pressurized fluid in at least one of said working chambers comprising a volume of pressurized gas.

Inventors: MINTGEN ROLF, MINTGEN, ROLF
Applicants: STABILUS GMBH
Application year: 1989
Main classification: F16F9
IPC codes: F16F9