Draw works control system

Description

[0001] This invention relates to control systems for hydraulically operated draw works having winches, or the like, and which may have hydromechanical boom or hook type draw works transmission controls.

[0002] Winches, or as more generally known, draw works, are used in a large variety of operations and, as a consequence, there are draw works constructions available with widely varying degrees of sophisticated control and drive equipment. Some of the more sophisticated draw works constructions are hydraulically operated and include a hydraulic motor for driving a draw works drum. Typically, there is provided a hydraulically disengaged brake which brakes the drum to prevent unduly rapid lowering of a load to be hoisted. A multiple-speed, hydraulically controlled transmission may interconnect the drum and the drive motor therefor.

[0003] There is also provided means for regulating the amount of control fluid applied to the hydraulically disengaged brake to control the degree of disengagement of such brake and thereby control the rate of descent of an elevated load.

[0004] In the usual case, two types of load-lowering are desirable. The first is the so-called "drop and catch" lowering wherein the brake is fully disengaged and the load is allowed to fall at its maximum rate. When the load has been lowered the desired amount, the brake is once again engaged and further lowering is arrested. The second type of lowering is the so-called "controlled" lowering in which the brake is only partially disengaged thereby allowing a load to be lowered at some controlled rate less than the maximum.

[0005] During the drop and catch lowering, initial engagement of the brake to cath the load will cause "grabbing" of the brake rather than smooth engagement. This, in turn, communicates a considerable shock to the internal components of the brake and draw works components connected to the output of the brake. This shock reduces the useful life of such components by causing premature wear and failure thereof.

[0006] It is therefore highly desirable therefore to prevent such shock loading by providing for gradual application of the brake in drop and catch lowering. DE-A-1431991 discloses the use of an accumulator in a control system for a winch brake which is hydraulically disengaged, the accumulator modulating application of the brake by means of a piston within the accumulator acted upon by a spring and acting on the hydraulic fluid in connection with the brake.

[0007] During controlled lowering, however, such a feature is not desirable since modulation of brake application will result in additional travel of the load after the operator applies the brake thereby making fine control of load position difficult. US-A-4048799 describes a control system for controlled lowering of a load. Moreover, such modulation is not necessary since changes in torque level are not so drastic as to cause the detrimental shock noted above.

[0008] It can be seen therefore that the two conditions of lowering involve different considerations and different solutions particularly as regards the application of the brake with or without modulation respectively.

[0009] According to the present invention, a control system for a spring-applied hydraulically-disengaged brake having a source of fluid under pressure; a control valve having a fluid inlet connected to the source of fluid and a fluid outlet; and an accumulator, is characterized in that the accumulator is connected between the fluid outlet of the control valve and the brake, the accumulator including a body having a bore, an inlet port in the body connected to the control valve, and outlet port in the body connected to the brake a piston slidably disposed in the bore, an accumulator chamber one one side of the piston in fluid communication with the outlet port, a spring pocket located on the other side of the piston; a spring positioned within the spring pocket and biasing the piston towards a predetermined position within the bore, means for connecting the inlet port with the spring pocket, and a metering orifice connecting the spring pocket with the accumulator chamber to permit, in use a continuous but limited rate of fluid flow between the outlet port and the inlet port.

[0010] One example of a control system according to the invention will now be described with reference to the accompanying drawings in which:

Figure 1 is a schematic view of the hydraulic control system illustrating mechanical details of manual actuators therefor;

Figure 2 is a sectional view of a control valve of the system, which also schematically illustrates peripheral components utilized in the system;

Figure 3 is a sectional view taken approximately along the line III-III of Figure 2; and,

Figure 4 is a sectional view of the accumulator which also schematically illustrates peripheral components.

[0011] One example of a control system for a hydraulically operated draw works or the like including a hydraulically disengaged brake, a multi-speed, hydraulically controlled transmission and a drum to be driven or braked is illustrated in the drawings and, with reference to Figure 1, is seen to include a multi-speed, hydraulically controlled transmission including a high speed section indicated schematically at 10 and a low speed section schematically indicated at 12. As will be seen, the transmission including the components 10 and 12 is of the type that when fluid under pressure is directed to the high speed section 10, the output speed of the transmission will be in high gear, and when fluid under pressure is directed to the low speed section 12, the output speed of the transmission will be in the low range.

[0012] The draw works assemblage includes a spring-engaged, hydraulically disengaged brake which may be of conventional construction and which is illustrated schematically at 14. The system also includes a metering pump 16 which will be suitably coupled to the draw works drum (not shown) through a one-way clutch (not shown) so as to be driven thereby when the load is lowered at a speed proportional to the rate of rotation of the draw works drum. The purpose of the metering pump 16 is to act as a governor and limit the rotational velocity of the drum.

[0013] When the draw works system is used in a vehicle as, for example, a pipe layer, there will be a number of additional hydraulically controlled components associated with the vehicle, which components are schematically illustrated at 18 and may include steering clutches, power transmission and vehicle brake elements. Fluid under pressure is provided to the system by a hydraulic pump 20, typically driven by the prime mover of the vehicle. The pump 20 receives oil from a reservoir 22 and directs the same, under pressure, to a junction 24. One side of the junction 24 extends to a priority valve 26 which, in turn, permits the flow of fluid to the vehicle components 18. The other side of the junction 24 extends to the control system of the present invention.

[0014] The priority valve 26 is of conventional construction and is operative to ensure delivery of fluid to the control system of the present invention at a pressure equal to or exceeding a predetermined minimum pressure. Frequently, hydraulic fluid flow requirements of the vehicle components 18 will cause the pressure to drop to a relatively low value which is insufficient to maintain engagement of the components of the transmission. The priority valve 26 prevents such from occurring.

[0015] The control system includes a control valve, generally designated 28, which comprises two valves in a common housing. Manual actuators, generally designated 30, are provided for the valve 28 in, for example, an operator area. The manual actuators 30 include, for example, a handle 32 which may be grasped by the operator to perform a variety of functions to be described. A console within the operator area is provided with a slot 34 in which the handle 32 may be moved.

[0016] A first mechanical link, shown schematically at 36, is attached to the handle 32 and extends to the control valve 28 to convey thereto mechanical motion of the handle 32 directing the secltion of a particular transmission output speed. A similar linkage, shown schematically at 38, extends to a brake control section of the valve 28 to convey mechanical movement of the handle 32 to the valve 28 to direct the flow of hydraulic fluid under pressure to the brake 14 to control its degree of disengagement.

[0017] A third linkage, shown schematically at 40, extends to a motor speed and direction control system (not shown) which is operative to control the speed of the hydraulic drive motor for the draw works as well as its directional output.

[0018] The linkages 36, 38 and 40 may be conventional in nature and, for example, in the form of control cables or linkages. It is only necessary that the linkage 36 be responsive to movement of the handle 32 in the right-left direction, as viewed in Fig. 1, and nonresponsive to other direction of movement thereof. The linkages 38 and 40 are similar, but are responsive only to up-down movements of the handle 32, as viewed in Fig. 1, and nonresponsive to left-right movement.

[0019] The slot 34 defines a shift pattern for the handle 32. It includes a horizontally elongate slot 42. When, as viewed in Fig. 1, the handle 32 is disposed in the left-hand end of the slot 42, the control valve 28 will direct the transmission to select its high speed output. When the handle 32 is in the right-hand extremity of the slot 42, it will direct the control valve 28 to select the low speed range of the transmission.

[0020] At each end of the slot 42, there are provided downwardly extending slots 44 and 46. When the handle 32 is aligned with either of the slots 44 and 46, and depressed therein, the linkage 40 will direct the motor speed and direction control system to drive the drum of the draw works to elevate the load. The degree of depression of the handle 32 in either of the slots 44 or 46 will control the speed of the drive motor for the winch.

[0021] Also included is an upwardly extending slot 48 intermediate the ends of the slot 42. When the handle 32 is aligned with the slot 48, a direction by the valve 28 to the transmission will cause the latter to assume a neutral condition. As the handle 32 is elevated in the slot 48, the brake 14 will be allowed to progressively disengage as the handle 32 moves further up the slot. At the same time the linkage 40 may be directed, after the backlash has been taken up, to drive the drum motor in a direction to lower the load at a particular speed, but only if the load is not of sufficient magnitude for gravity to overcome the friction of the draw works assemblage.

[0022] A short, downwardly extending slot 50 intersects the slot 42 intermediate its ends. WHen the handle 32 is directed downwardly into the slot 50, there will be a direction to the motor speed and direction control system to energize the drive motor for the draw works.

[0023] Returning to the junction 24, hydraulic fluid under pressure is directed along a line 52 to the transmission control side of the valve 28 in a manner to be described in greater detail hereinafter. It is also directed to a check valve system 54. The check valve system 54 includes a first check valve 56 which precludes backflow from any downstream component to the junction 24. Just downstream of the check valve 56 there is located a junction 58. Connected to the junction 58 is a check valve 60 which extends to the metering pump 16. The check valve 60 precludes discharge of an accumulator 62 except through the valve 28.

[0024] Turning now to Figures 2 and 3, the construction of the control valve 28 will be described in greater detail. The valve 28 includes a housing 100 formed of a center housing 102, a right end housing 104 and a left end housing 106. The left end housing 106 receives, in a conventional fashion, cable ends 108 and 110 of the linkages 36 and 38, respectively. The center housing 100 includes a transmission control bore 112 and a brake control bore 114. The housing 104 includes cavities 116 which are aligned with the bores 112 and 114 and house bi-directional spring centering assemblies 118 which are operative to center respective ones of a transmission control spool 120 in the bore 112 and a brake control spool 122 in the bore 114 to the positions illustrated in Figure 2 regardless of whether the spools 120 and 122 have been shifted to the right or to the left.

[0025] The spools 120 and 122 have leftward extensions which extend into the housing 105 for connection to the cable ends 108 and 110 whereby the spools 120 and 122 may be shifted to the right or to the left in in their bores by manipulation of the handle 32, as mentioned previously.

[0026] The transmission control spool 120 does not need to be further described for the purposes of the present invention.

[0027] Turning now to the brake control section of the valve 28, the brake control bore 114 includes a cavity 150 which is connected to junction 58 for receipt of fluid under pressure. Just to the right of the cavity 150 as seen in Fig. 2, is an outlet port 152 which is adapted to be connected to both a brake accumulator 174 and to the metering pump 16, as shown in Fig. 4. The outlet port 152 is disposed between the cavity 150 and the outlet port 132 which extends to the reservoir 22.

[0028] The spool 122 includes a land 158 having a relatively long axial length which is normally operative to preclude the flow of fluid from the cavity 150 to the outlet port 152 while allowing flow of fluid from the outlet port 152 to drain through the drain port 132 or to interrupt fluid communication between the drain port 132 and the outlet port 152 and allow fluid to flow from the cavity 150 to the outlet port 152 under circumstances to be described in greater detail hereinafter.

[0029] As seen in Figs. 2 and 3, the land 158 includes oppositely disposed, axially extending grooves 160, 162 and 164 in its periphery. Each of the grooves 160, 162 and 164 opens to the inlet side of the land 158 and, as can be best seen in Fig. 2, the groove 160 has a relatively long axial length, the groove 162 has an intermediate axial length, while the groove 164 has a relatively short axial length. As seen in Fig. 3, the grooves 162 and 164 have relatively large cross sections, while the groove 160 has a relatively small cross section. Moreover, all three grooves have a progressively decreasing cross section from left to right (Fig. 2).

[0030] In the case of a brake in a draw works, it is desired that there be an infinite number of degrees of disengagement so that the speed of descent of the load can be regulated. The grooves 160, 162 and 164 serve as metering grooves to assist in attaining such a degree of brake disengagement control. Specifically, the further the spool 122 is moved to the right, as viewed in Fig. 2, the greater the fluid flow from the cavity 150 to the outlet 152 through the grooves 160. The greater the fluid flow, the greater the degree of disengagement of the brake 14 which, it will be recalled, is of the hydraulically disengaged type. For greater rightward shifts of the spool 122 within the bore 114, fluid communication between the cavity 150 and port 152 will be established through the larger groove 162 so that fluid flow will be less restricted. For even greater rightward shifts of the spool 122, fluid communication between the cavity 150 and port 1 52 will be established through all three grooves 160, 162 and 164. Fluid flow will then be at its maximum allowing the load to be lowered at its maximum rate.

[0031] To enable the operator to feel when the condition of maximum lowering rate is being approached, a spring 166 has been included to provide positive feedback to the operator. As the leading edge of the groove 164 approaches the leftmost surface of cavity 168 which leads to port 152, the washer 167 contacts a shoulder 170 of the bore 114. Any further rightward movement of spool 122 compresses the spring 166 and provides for a positive operator feel when the maximum speed groove 164 has been entered.

[0032] As best seen in Figs. 1 and 4, fluid flowing from the port 152 will flow to a junction 172 and simultaneously to the metering pump 16 and a brake accumulator, generally shown at 174.

[0033] As explained above, the brake is of the spring engaged-hydraulically disengaged type and therefore the brake 14 may be disengaged, with the load lowered, only by supplying brake 14 with hydraulic fluid from the port 152. In such a brake, the greater the fluid pressure the greater the degree of disengagement and the greater the quantity of fluid required to cause progressive disengagement. As shown in Figs. 1 and 4, the brake 14 can only be supplied with hydraulic fluid through the brake accumulator 174.

[0034] Hydraulic fluid metered through the grooves 160, 162 and 164 is supplied to a brake accumulator port 176 in a housing 178 of the accumulator 174. Located within the housing 178 is a bore 180 which contains a piston 182. The piston 182 has a relatively thin wall 184 which is perforated by a number of passageways 186. As viewed in Fig. 4, the piston is urged to the left by springs 188 and 190.

[0035] When fluid is supplied to the port 176, it will flow through the piston passageways 186 and into a spring pocket 192. The spring pocket 192 is ultimately connected to the brake 14 by a passageway 194, a check valve 196, an accumulator chamber 198 and an accumulator port 200.

[0036] Located within the brake 14 is a brake release piston 202, a brake return spring 204 and a brake cylinder 206. The brake 14 is otherwise conventional in construction and need not be further explained. It is sufficient to note that when the piston 202 is in the leftmost position, as viewed in Fig. 4, the brake 14 will be fully applied and as the piston 202 is forced an increasing distance to the right by pressurized fluid in the cylinder 206, the brake 14 will be increasingly released.

[0037] The piston return spring 204 creates a force opposing fluid pressure in the cylinder 206. Therefore, if fluid pressure in chamber 206 is in- suficient to overcome the force created by the spring 204, the piston 202 will be urged to the left and the brake 14 will be. applied.

[0038] As stated above, the pressure of the hydraulic fluid supplied from the outlet port 152 to the accumulator port 176, and consequently the brake 14, may be varied by operator actuation of the brake spool 122. Depending on the pressure of fluid supplied to the brake 14, brake release will be accomplished by one of two methods. If fluid supply pressure is high, the force on the piston 202 will be sufficient to completely overcome the force created by the spring 204. In this case, the brake piston 202 will be forced fully to the right and the brake 14 will be completely released. As a consequence of this large piston 202 movement, a large volume of hydraulic fluid will enter the brake cylinder 206.

[0039] A relatively low hydraulic fluid pressure will be insufficient to completely overcome the force created by the return spring 204 and the brake piston 202 will be forced only a short distance to the right. This piston movement will be insufficient to completely release the brake 14 but will cause slippage. In this situation, the volume of fluid entering the piston cylinder 206 will be relatively small.

[0040] As will be seen in Fig. 2, when the brake spool 122 is returned to the neutral position, the outlet port 152 will be connected to the relief port 132 and consequently to the tank 22. This will cause the pressure of the fluid supplied to the accumulator port 176, and consequently the spring chamber 192, to drop to a very low level. The pressurized fluid remaining in the accumulator chamber 198 and the brake cylinder 206 will then cause the check valve 196 to seat, precluding reverse fluid flow through the spring chamber 192. All fluid from the brake 14 will thus be forced through the chamber 198 and towards the left end of the piston 182.

[0041] Located on the piston 182 are piston surfaces 208 and 210 upon which the fluid located in the accumulator chamber 198 will act. Located within a piston wall 212 is a metering orifice 214 which establishes fluid communication between the accumulator chamber 198 and the accumulator port 176 through the piston passageways 186.

[0042] When the pressure of fluid supplied to the brake 14 is relieved, reverse flow to the tank 22 through the ports 1 52 and 132 will be accomplished by one of two modes depending upon the volume of fluid contained in the piston cylinder 206.

[0043] If the pressure, and therefore the volume, of fluid located in the brake cylinder 206 is low, as is the situation during controlled lowering when the brake 14 is only partially released, there will be insufficient fluid in the accumulator chamber 198 and brake cylinder 206 to fully compress the springs 188 and 190. Therefore, while the accumulator piston 182 will travel a slight distance to the right, this travel will not compress the springs 188 and 190 far enough to create a fluid backpressure within the accumulator chamber 198 and brake cylinder 206 sufficient to cause slippage of the brake 14. Any fluid located in the accumulator chamber 198 and the brake cylinder 206 will simply flow through the metering orifice 214 as the piston 182 slowly moves to the left and will be ultimately returned to the tank 22 through the control valve 28.

[0044] If the pressure, and therefore the volume, of fluid supplied to and entering the brake 14 is large, as when the brake 14 is fully released, reverse flow to the control valve 28 will be somewhat different. In this situation, fluid pressure in the accumulator chamber 198 and the brake cylinder 206 will be sufficient, when acting on the accumulator piston surfaces 208 and 210, to fully compress the springs 188 and 190. As the piston surface 208 moves beyond a port edge 216, the accumulator piston 182 will act as a relief valve and allow a large volume of fluid to flow to the accumulator port 176. As the residual pressure in the brake 14 and the accumulator chamber 198 decreases, the springs 188 and 190 will once again force the piston 182 to the left. The springs 188 and 190 are chosen such that the force on the piston 182 will cause a backpressure in the accumulator chamber 198 and the brake cylinder 206 sufficient to maintain slippage in the brake 14.

[0045] Once the piston 182 has been urged a short distance to the left, the accumulator chamber 198 will no longer be in direct fluid communication with the port 176 and any remaining fluid in the accumulator chamber 198 and the brake cylinder 206 must flow through the metering orifice 214 and the piston passageways 186. The metering orifice 214 will limit the flow of fluid from the piston cylinder 206 and thus cause gradual application of the brake 14.

[0046] In operation, there will be two distinct modes of load lowering available to the operator. The first is "drop and catch" lowering where it is desired to lower the load for a distance at the maximum rate available and then arrest lowering at a particular point. The second mode is "controlled" lowering where it is desired to lower a load at a speed somewhat less than the maximum available. As described above, when lowering at the maximum rate is desired, the brake spool 122 will be in the rightmost position as viewed in Fig. 2. High pressure fluid will be allowed to flow through the grooves 160, 162 and 164 from the cavity 150 to the outlet port 152. As shown in Fig. 4, fluid flow from the outlet port 152 will proceed to the junction 172 and then to the accumulator port 176 and the metering pump 16. Upon reaching the accumulator port 176, the fluid flows through the piston passages 186, the spring pocket 192, the passageway 194, the check valve 196 and finally through the accumulator port 200 to the brake cylinder 206. The accumulator chamber 198 will become completely filled during this process.

[0047] Since fluid pressure and flow is at its maximum, the brake piston 202 will be forced completely to the right and the brake 14 will be fully released. The load will therefore drop at its maximum rate.

[0048] When it is desired to stop descent of the load, the brake spool 122 is shifted to the neutral position as shown in Fig. 2. As indicated above, the outlet port 152 will then be in fluid communication with the drain port 132, and consequantly, the tank 22. The accumulator spring pocket 192 and the passageway 194 with thus be drained by the drain port 132. Fluid pressure in the accumulator chamber 198 and the piston cylinder 206 will then cause the check valve 196 to be completely seated.

[0049] Since the check valve 196 is closed, all hydraulic fluid to be discharged from the brake 14 must move the accumulator piston 182 against the springs 188 and 190. Since the fluid pressure in the accumulator chamber 198 and the piston cylinder 206 is high, the fluid acting upon the piston surfaces 208 and 210 will create a force sufficient to fully compress the springs 188 and 190.

[0050] As the piston 182 moves to the right, the piston surface 208 will clear the edge 216 of the port 176 and the piston 182 will act as a relief valve. As the pressure of fluid in the accumulator chamber 198 and the piston cylinder 206 decreases, the springs 188 and 190 will force the piston 182 to once again move towards the left, closing off accumulator port 176.

[0051] Since the springs 188 and 190 are greatly compressed, they will cause the piston 182 to act upon fluid contained in the accumulator chamber 198 with a force sufficient to cause a fluid backpressure in the accumulator chamber 198 and the piston cylinder 206 such that the brake 14 will continue to slip.

[0052] With the accumulator chamber 198 no longer in direct fluid communication with accumulator port 176, any further fluid flow from the accumulator chamber 198 and the brake cylinder 206 must be through the metering orifice 214. The limited flow through the metering orifice 214 will cause the gradual relief of fluid pressure in the brake cylinder 206 and thus provide modulated brake application and gradual arrest of the load.

[0053] During controlled lowering, fluid flow from the cavity 150 to the outlet 152 will be through less than all of the grooves 160, 162 and 164. This will generate a fluid pressure in the brake cylinder 206 which will be less than that required to completely release the brake 14. However, fluid pressure in the cylinder 206 will be of a magnitude that will cause slippage and limited rotation of the brake 14. Since the brake piston 202 will move only a slight distance to the right, a relatively small volume of fluid will be contained in the brake cylinder 206.

[0054] When the brake valve 122 is returned to the neutral position, fluid flow from the accumulator chamber 198 and the piston cylinder 206 will once again be limited to the left end of the piston 182 by action of the check valve 196.

[0055] Since during controlled lowering the pressure and volume of fluid contained in brake cylinder 206 is low, the volume of fluid acting on the piston surfaces 208 and 210 will not fully compress springs 188 and 190. Therefore, the springs 188 and 190 will not be compressed a distance sufficient to create the backpressure required to cause an indicated slippage of the brake 14. Brake application will be immediate.

[0056] It will thus be seen that the addition of the accumulator 174 to a draw works control system will provide the dual advantages of modulated braking during high-speed lowering and unmodulated rapid brake application during controlled lowering.

Claims

1. A control system (28) for a spring-applied hydraulically-disengaged brake (14) having a source of fluid (20) under pressure; a control valve (114, 122) having a fluid inlet (156) connected to the source of fluid and a fluid outlet (152); and an accumulator characterized in the accumulator (174) is connected between the fluid outlet (152) of the control valve and the brake (14), the accumulator including a body (178) having a bore (180), an inlet port (176) in the body (178) connected to the control valve (114, 122), an outlet port (200) in the body (178) connected to the brake (14), a piston (182) slidably disposed in the bore (180), an accumulator chamber (198) on one side of the piston in fluid communication with the outlet port (200), a spring pocket (192) located on the other side of the piston; a spring (188, 190) positioned within the spring pocket (192) and biasing the piston towards a predetermined position within the bore, means (186, 216) for connecting the inlet port (176) with the spring pocket (192), and a metering orifice (214) connecting the spring pocket (192) with the accumulator chamber (198) to permit, in use a continuous but limited rate of fluid flow between the outlet port (200) and the inlet port (176).

2. A control system according to claim 1, wherein the piston (182) has a hollow interior and wherein the metering orifice (214) is located in the piston extending from the hollow interior (184) of the piston to the outer surface of the piston.

3. A control system according to claim 2, wherein the means (186, 216) for communicating the first port (176) with the spring pocket (192) includes a passageway (186) extending from the hollow interior (184) of the piston (182) to the outer surface.

4. A control system according to any of claims 1 to 3, further including a check valve (196) located between the spring pocket (192) and the accumulator chamber (198) to permit unrestricted fluid flow through the check valve from the spring pocket (192) to the accumulator (198) and to prevent fluid flow from the accumulator chamber (198) to the spring pocket (192) except for the flow through the metering orifice.

Revendications

1. Système de commande (28) pour un frein (14) à serrage par ressort et à desserrage hydraulique ayant une source de fluide sous pression (20); une valve de commande (114, 122) ayant une entrée de fluide (156) reliée à la source de fluide et une sortie de fluide (152); et un accumulateur (174), caractérisé en ce que l'accumulateur (174) est connecté entre la sortie de fluide (152) de la valve de commande et le frein (14), l'accumulateur comprenant un corps (178) ayant un alésage (180), un orifice d'entrée (176) dans le corps (178) relié à la valve de commande (114, 122), un orifice de sortie (200) dans le corps (178) relié au frein (14), un piston (182) disposé à glissement dans l'alésage (180), un chambre d'accumulateur (198) d'un côté du piston en communication de fluide avec l'orifice de sortie (200), un logement de ressort (192) situé de l'autre côté du piston; un ressort (188, 190) placé dans le logement de ressort (192) et sollicitant le piston vers une position prédéterminée dans l'alésage, un moyen (186, 216) pour relier l'orifice d'entrée (176) au logement de ressort (192), et un orifice de réglage (214) reliant le logement de ressort (192) à la chambre d'accumulateur (198) afin de permettre, pendant l'utilisation, une circulation de fluide à un continu mais limité entre l'orifice de sortie (200) et l'orifice d'entrée (176).

2. Système de commande selon la revendication 1 dans lequel le piston (182) a un intérieur creux et dans lequel l'orifice de réglage (214) est logé dans le piston, s'étendant de l'intérieur creux (184) du piston à la surface extérieure du piston.

3. Système de commande selon la revendication 2, dans lequel le moyen (186, 216) pour faire communiquer le premier orifice (176) avec le logement de ressort (192) comprend un canal (186) s'étendant de l'intérieur creux (184) du piston (182) à la surface extérieure.

4. Système de commande selon l'une quelconque des revendications 1 à 3, comprenant en outre une valve antiretour (196) disposée entre le logement de ressort (192) et la chambre d'accumulateur (198) afin de permettre une circulation sans restriction du fluide à travers la valve antiretour du logement de ressort (192) à l'accumulateur (198) et d'empêcher une circulation de fluide de la chambre d'accumulateur (198) au logement de ressort (192), abstraction faite de la circulation à travers l'orifice de réglage.

Ansprüche

1. Steuersystem (28) für eine federangelegte hydraulisch außer Eingriff bringbare Bremse (14) mit einer unter Druck stehenden Strömungsmittelquelle (20), einem Steuerventil (114, 122) mit einem Strömungsmitteleinlaß (156), verbunden mit der Strömungsmittelquelle und einem Strömungsmittelauslaß (152) und mit einem Akkumulator, dadurch gekennzeichnet, daß der Akkumulator (174) zwischen den Strömungsmittelauslaß (152) des Steuerventils und die Bremse (14) geschaltet ist, wobei der Akkumulator einen Körper (178) mit einer Bohrung (180) aufweist, sowie mit einer Einlaßöffnung (176) im Körper (178) verbunden mit dem Steuerventil (114, 122), einer Auslaßöffnung (200) im Körper (178), verbunden mit der Bremse (14), einen Kolben (182), gleitbar angeordnet in der Bohrung (180), ein Akkumulatorkammer (198) auf einer Seite des Kolbens in Strömungsmittelverbindung mit der Auslaßöffnung (20), eine Federtasche (192), angeordnet auf der anderen Seite des Kolbens, eine Feder (188, 190), positioniert innerhalb der Federtasche (192) und den Kolben in eine vorbestimmte Position innerhalb der Bohrung vorspannend, wobei ferner Mittel (186, 216) vorgesehen sind, um die Einlaßöffnung (176) mit der Federtasche (192) zu verbinden, und wobei schließlich eine Zumeßöffnung (214) die Federtasche (192) mit der Akkumulatorkammer (198) verbindet, um zu gestatten, daß bei Benutzung eine kontinuierliche aber begrenzte Strömungsmittelflußrate zwischen der Auslaßöffnung (200) und der Einlaßöffnung (176) auftritt.

2. Steuersystem nach Anspruch 1, wobei der Kolben (182) eine hohles Inneres besitzt, und wobei die Zumeßöffnung (214) im Kolben angeordnet ist, und zwar sich vom hohlen Inneren (184) des Kolbens zur Außenoberfläche des Kolbens hin erstreckend.

3. Steuersystem nach Anspruch 2, wobei die Mittel (186,216) zur Verbindung der ersten Öff- nung (176) mit der Federtasche (192) einen Durchlaß (186) aufweisen, der sich vom hohlen Inneren (184) des Kolbens (182) zu der Außenoberfläche hin erstreckt.

4. Steuersystem nach einem der Ansprüche 1 bis 3, mit einem Rückschlagventil (196), angeordnet zwischen der Federtasche (192) und der Akkumulatorkammer (198), um den uneingeschränkten Strömungsmitteifluß durch das Rückschlagventil von der Federtasche (192) zum Akkumulator (198) zu gestatten und um den Strömungsmittelfluß von der Akkumulatorkammer (198) zur Federtasche (192) zu verhindern, mit Ausnahme des Flußes durch die Zumeßöffnung.

Drawing