DE2060091A1 - Thermally controlled spring - Google Patents

Description

Thermally controlled spring.

Known are thermally controlled gas springs, whose spring force by Change in temperature of the resilient medium is adapted to variable loads. Even thermal springs git transmission of the controlling forces by mechanical and hydraulic Linkages are known, as are thermo-electrically controlled gas springs and spring systems with separate evaporation and condensation rooms and associated feeding equipment for the resilient medium, and systems that accelerate the control processes Operate the heat accumulator. All known systems regulate the load-bearing capacity of the spring in such a way that increasing load is absorbed by increasing the temperature.

According to the invention, the volume of the controlling medium is divided up into at least 2 smaller volumes, which are arranged and switched in such a way that part of the available controlling volume (e.g. gas or steam weight) the load-bearing spring system of any kind, e.g. Stahliedern or Luitiedern or also Ruflifedern or several combined in the sense of a relief, and another Volume acts inversely in the sense of a load, the carrying capacity of the controlled Spring system to an average value between maximum and minimum load capacity is measured. The distribution of the controlling media can be so eriolgen that a part in a thermally influenceable control energy generating space, and a other part in a known spring pressure accumulator (e.g. gas pressure accumulator) is housed. The controlling medium is even more advantageous in at least the second thermally influenced rooms housed, the i previously described senses work in push-pull that one room is heated for the purpose of increasing the pressure, and at the same time the other room is being cooled, and the differential pressure between these two rooms serves as a controlling force. Such a regulating and control device according to the invention in connection with an appropriately sized spring system has the following advantage compared to previously known systems.

i) The Hegel speed is determined by the push-pull effect described above greatly increased.

2) The starting point of the control processes during commissioning colder Vehicles is the height position of the load-bearing which corresponds to an average load condition Spring system. The vehicle will usually be immediately operational and cushioned reach the optimal level faster.

3) The differential pressure between the controlling rooms determines the Desired height control, not an absolute pressure to be achieved. The system does not always need to be brought to a temperature level determined by the load will. When the vehicle is cold, it can also work in the lower temperature range.

4) It is possible without anyone - for example with electrical contacts working - special control pulse generator between vehicle axles and thermal started to work with the control device, only two thin pipes, e.g. as hydraulic linkage, are between the spring control rooms on the axles and the thermal control device required 0 5) Constructive combinations of suspension, Control device and vibration damper are easy to implement.

An exemplary embodiment is shown in FIGS. 1, 3 and 4 with the remark that consciously in the interest of the intelligibility of the practical structural design and their dimensions strongly deviating schematic representations were chosen. The vehicle body rests on wheel (i) with axle (2), supported by a spring (3) (4). Spring (3) is dimensioned so that its normal arrow height under static load the empty weight plus about 1/3 to 2/3 of the payload depending on the vehicle type and - usage corresponds. In the following, as an example with curb weight + 1/2 Payload calculated. The vehicle is now too high with its empty weight and with full load too deep. The spring height control system shown in Fig attached, consisting of the additional spring (5), the cylinder (6) with piston and piston rod (7), the two pipes (8 and 9), the thermally controlled cylinders (io u0ii) with the pistons (12 and 13), the heating elements (14 and 15) and the cooler (16), plus the example of a control shown in Fig. 3 and 4, to which is received.

When the vehicle is 1/2 loaded, the body (4) is at the correct height the matching spring characteristic of the spring (3). The tension and compression spring (5) is in the middle position of the piston (7) in the cylinder (6) without tension, in front and behind Piston (7) has the same fluid pressure as the thermally controlled cylinder (10 and 11) have the same pressure at the same (rest) temperature. In the cylinders (io u.ii) is located under the pistons in the spaces with the heat exchangers (14 and 15) a Frigen s.B. Frigen 115 Pentafluoromonochloroethane (CF3 - CF2Cl), or the similar Frigen 22, with which the example is calculated, since the steam tables are better known for this. The heat exchangers (14) and (15) are used by the engine cooling water heated (assumed 850) resp. from the one previously re-cooled in the cooler (16) to approx. 45 Cooling water flowed through. The supplied and removed amount of heat is with the help controlled by the control device (Fig. 3 and 4). This consists of the Biffenenz pressure controlled Piston (20) with springs (22) and (23) in cylinder (21) and the control piston (24) in cylinder (25) for controlling the hot and cold water supply to the heat exchangers (14) and (15) with cooler (16). Control unit (24/25) is activated once via the knee lever (28) of the piston (20) and, on the other hand, of the - depending on the two piston positions the pistons (12) and (13) of the cylinders (io) and (ii) moving control levers (26), all of which act on the piston rod $ (27) of the control piston (24). Pistons (2c) in cylinder (21) is against the force of the springs (22/23) of the liquid keitsdruckdifferenz in the lines (8/9) of the hydraulic linkage between the cylinder (6) and the cylinders (lo / il) moved, the differential pressure of the pressures in front and behind Piston (20) precisely determines its position. The piston (24) in the cylinder (25) is finally from the piston (20) the two control levers (26) and the return spring (39) set so that the required heating and cooling water flow rate value the specified differential pressure upstream and downstream of the piston (7) and the piston position the working piston (12) and (13) corresponds to what the latter via the pipelines (8/9) then the positive or negative required for the normal height of the structure (4) Set the additional spring force of the spring (5).

If the structure (4) is now pushed down against the spring (3) is pressed, the spring (5) is also compressed.

The pressure equilibrium in front of and behind piston (7) is disturbed.

The pressure in line (8) rises, which falls in line (9) 0 The control piston (20) in cylinder (21) is moved downwards.

Because the lever (26) initially remains in the piston position (12/13) are stationary, the piston (20) presses the piston rod via the toggle lever (28) (27) to the right. Slider (24) opens somewhat to the flow of hot water to the heat exchanger (15) and after cooling in (16) the cold water inflow to (14). That warmed Frigen in cylinder (11) partly evaporates, that in cylinder (io) partly condenses the different Steam pressure in cylinder (11 / 1o) moves piston (7) downwards and tensions spring (5§so on pressure that the normal altitude of structure (4 is reached again now prevailing diflerential pressure in front of and behind piston (20) would heat the Cylinder (left) do not go on exactly limited and thus too high a piston position of the piston (13) with an indentation that goes beyond what is required for the load of the piston (7) can occur with the pretension of the spring (58). This prevents the return of the piston rod (27) with control piston (24) by the dependent on the height position of the working piston (13) in cylinder (ii) moved lever (26) left, whereby always for a certain differential pressure in front of and behind the control piston (20) also a very specific height position of the pistons (13) and (12) in the working cylinders (ii) and (io) and thus again a very specific height of the piston (7) and thus bias of the spring (5) - on tension or pressure - is set.

It would be, which is also conceivable, at the beginning of the load change process not only moves the piston (20) down, but also the working piston (13) pressed down in cylinder (11), this would start the opening process of the hot water inflow through (24) to (15) only accelerated to working piston (13) now going up again throttles the hot water flow via lever (26). The lever (26) is held in the nut (30) by the rod (29) provided with an inclined groove. panned.

If too much heat was supplied to the heat exchanger (15), the system overridden, the control piston (24) would not only supply hot water to (15) tie, but go even further to the left and reverse the flow of water, so that the heat exchanger (14) is now heated and (is) cooled until the rest position is reached is. Throttle bores (31) in lines (8) and (9) prevent unwanted oscillation of the thermal system.

When the superstructure (4) is relieved, the described control and control processes in some cases vice versa. As for the control the difference of the in front of and behind the control piston (20) prevailing pressures in connection with the spring forces of the springs (22/23) in cylinder (21) is decisive in connection with the height position the working piston (12/13) and since this pressure difference also the position of the piston (7) and thus the preload of the spring (5), it comes to the level of the absolute Don't press at all. i.e. the system is already effective at the start of operation with very low temperatures, because the suitable Frigen already shows when it is cold working vapor pressures.

Naturally, when using the invention described, thoughts are taken Numerous other structural designs are also possible.

For example, an arrangement similar to Fig. 2 can also be selected if you want to combine shock-absorbing effects with the spring and level control system. Here structure (4) was over Spring (3) supported on axle (2) in such a way that cylinder (55) can be placed over spring (3). Piston (54) runs in cylinder (55) and is connected to axle (2) via rod (53) arranged inside spring (3). The spaces above and below the piston (54) are again connected to the regulating and control device via the throttle bores (31) and pipes (8/9), as already described. In order for the spring (3) to work, the compressed gas cushion (5f) separated by the floating piston (a7) and the gas cushion in the annular space (58), the working spaces above the piston (54) and below the same - are also common in shock absorber construction The short-term movement impulses coming from the spring movement of the ender (3) are processed here in connection with the usual shock absorber valves etc. The level control system otherwise works as already described.

To explain the working area and the dimensions of a control system According to Fig. 1, 3 and 4 of the invention, the following approximate for a car rear axle determined data.

Assumptions: Empty load 2 * 400 = 800 kg 1/2 load 2. 540 = 1080 kg diff. 2. 140 = 280 kg full load 2. 680 = 136o kg "2 0 280 = 560 kg Calculated with Frigen 22, which has similar vapor table values as the even more suitable Frigen 115 (C2F5Cl) boiling point -38 ° C temperatures -38 ° -25 ° 0 ° 50 ° 80 ° pressures ata i 2 5 20 36 vol.fl.l / kg o, 7 o, 73 o, 77 o, 92 i, 1 n steam m3 / kg o, i9 o, 11 o, o47 o, oli o, oo45 enthalpy i 'Kcal / kg 90 93 100 116 127 "i" "/" 145 146.8 149.4 152.3 152.3 Required dimensions.

Piston area for + 280 kg at 50-80 ° C temperature difference - = 280: (36 - 20) = 18 cm2 due to a piston rod of 12 mm corresponding to 1, i cm2 are selected a total of 20 cm2 = 50 mm cylinder diameter.

For a stroke of + 70 mm the volume becomes V = 280 cm3 for both Wheels of the rear axle results in the volume of the working cylinder (lo / li) with each 560 cm3, for the oil-filled effective part.

Dimensions of the system for example for cylinder (6) with piston (7) each Wheel 180 mm high with 50 mm inner diameter.

For the working cylinders (io) and (11) each about 200 mm high at 72 mm inner diameter.

In addition, the control and regulation system, their cross-sections as well as the the piping and the dimensions of the small cooler in view of the small Flow rates become very small.

energy requirement for a full control process from 50 to 80 C des needed Frigens including its heat of vaporization Amount of frigen for volume steam at 80 ° C corresponding to 4500 cm3 / kg = 560: 4500 = 0.125 kg heat of evaporation i '' = (152 -116) # 0.125 = 4.5 Kcal This corresponds to a usable temperature gradient of 300 and a heat exchanger efficiency of 0.8 a heating water requirement of only about 0.19 ltr.

Claims (8)

Claims. 1). Thermally regulated spring system, characterized by several controlling volumes (io / li), one of which (io) in the sense of a discharge and a other (is) acts in the sense of a load on the spring system to be controlled (3/5). 2). Spring system according to claim 1 characterized by simultaneous Action of the volumes (io / ii) in push-pull as a result of a temperature increase in one volume with simultaneous @ temperature reduction in the other volume. 3). Spring system according to claim 1 and 2 characterized by an in The spring system determined their size from the differential pressure between the spaces (10/11) regulating force. 4) 0 spring system according to claim i to 3 characterized by a control member with control element (20), which is moved by the differential pressure, control elements (26), which are actuated by the height position of the pistons (12 / 1p) and control element (24) which of the first two members set the 1st heat supply and discharge to the thermally controlled rooms of the system. 5). Spring system according to Claims 1 to 4, characterized by the arrangement an intercooler (16) in the heating medium circuit via the control member (24). 6). Spring system according to claim i, characterized by the presence only a thermally regulated volume, which in the sense of a load on the to controlling spring acts. 7). Spring system according to Claims 1 to 6, characterized by the assembly of the spring force control element (54) with devices of a vibration damper (Fig.2). 8th). Spring system according to Claims 1 to 7, characterized by the arrangement throttling members (31) between the spring control part (6 and 55) and the thermal Control section (10/11) L e r s e i t e