Classifications

• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
  • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
  • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
  • E05F3/10—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes with a spring, other than a torsion spring, and a piston, the axes of which are the same or lie in the same direction
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
  • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
  • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
  • E05F3/10—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes with a spring, other than a torsion spring, and a piston, the axes of which are the same or lie in the same direction
  • E05F3/102—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes with a spring, other than a torsion spring, and a piston, the axes of which are the same or lie in the same direction with rack-and-pinion transmission between driving shaft and piston within the closer housing
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
  • E05F3/00—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices
  • E05F3/04—Closers or openers with braking devices, e.g. checks; Construction of pneumatic or liquid braking devices with liquid piston brakes
  • E05F3/12—Special devices controlling the circulation of the liquid, e.g. valve arrangement
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
  • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
  • E05Y2800/34—Form stability
  • E05Y2800/342—Deformable
  • E05Y2800/344—Deformable elastically
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
  • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
  • E05Y2800/40—Physical or chemical protection
  • E05Y2800/414—Physical or chemical protection against high or low temperatures
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
  • E05Y2800/00—Details, accessories and auxiliary operations not otherwise provided for
  • E05Y2800/67—Materials; Strength alteration thereof
  • E05Y2800/676—Plastics
  • E05Y2800/678—Elastomers
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
  • E05Y2900/00—Application of doors, windows, wings or fittings thereof
  • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
  • E05Y2900/13—Type of wing
  • E05Y2900/132—Doors
• • E—FIXED CONSTRUCTIONS
  • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
  • E05Y—INDEXING SCHEME ASSOCIATED WITH SUBCLASSES E05D AND E05F, RELATING TO CONSTRUCTION ELEMENTS, ELECTRIC CONTROL, POWER SUPPLY, POWER SIGNAL OR TRANSMISSION, USER INTERFACES, MOUNTING OR COUPLING, DETAILS, ACCESSORIES, AUXILIARY OPERATIONS NOT OTHERWISE PROVIDED FOR, APPLICATION THEREOF
  • E05Y2900/00—Application of doors, windows, wings or fittings thereof
  • E05Y2900/10—Application of doors, windows, wings or fittings thereof for buildings or parts thereof
  • E05Y2900/13—Type of wing
  • E05Y2900/132—Doors
  • E05Y2900/134—Fire doors

Definitions

• the invention relates to a drive for a sash of a window or door, in particular a door closer, comprising a drive mechanism for moving the sash, a drive housing in which the drive mechanism is at least partially arranged, and a hydraulic fluid, in particular oil, which is received in the drive housing, according to the preamble of claim 1.
• a drive of the type mentioned at the beginning is made of DE 195 15 169 A1 known.
• the drive mechanism typically comprises an output shaft rotatably mounted around a pivot axis, a linearly displaceable piston coupled to the output shaft which rotates the output shaft when displaced, and a compression spring with a first end and a second end, which supports the piston with its first end and exerts a compression spring force on it.
• Actuators for moving a window or door sash, especially door closers are typically filled with a hydraulic fluid (mostly mineral oil-based) to achieve a defined damping characteristic.
• a hydraulic fluid mostly mineral oil-based
• the hydraulic fluid heats up, for example due to climatic conditions or a fire, it expands. Since hydraulic fluid is incompressible, this heating leads to a pressure increase within the actuator. At excessively high pressures, the actuator's seals can fail, causing the hydraulic fluid to leak out. Furthermore, excessive pressure could also lead to the actuator bursting.
• a door control device for use on the fire-free side of a fire door, which is mounted in a door frame within a fire door safety assembly
• the door control device comprises a door closer assembly filled with a hydraulic damping fluid and mounted on the fire-free side of the fire door by means of at least one fastening element.
• the door control device also includes a door control arm pivotally connected at a first end to the door frame and at a second end to the door closer assembly.
• the hydraulic damping fluid is a fire-resistant hydraulic fluid.
• the door control device includes a pressure equalization device such that, when heated by contact between the door closer and the fire door, the hydraulic damping fluid within the door closer occupies a low-pressure volume, and any pressure generated therein is relieved by thermal expansion.
• the invention is based on the objective of creating a drive in which the disadvantages of the prior art do not occur, in particular in which the pressure within the drive does not rise impermissibly over a large temperature range, without disturbing the hydraulic functions.
• the drive unit has a volume compensation element arranged within the drive housing, wherein the volume compensation element comprises a compensation housing that is at least partially filled with a gas, in particular air, wherein the compensation housing has an outlet opening through which the hydraulic fluid flows into the volume compensation element under compression of the gas when the fluid temperature increases and flows out of the volume compensation element under expansion of the gas when the fluid temperature decreases, wherein a rolling diaphragm is provided within the compensation housing, which retains the gas in the compensation housing and hermetically separates it from the hydraulic fluid, and which, when the hydraulic fluid flows through the outlet opening, creates a flow path through the The flowing hydraulic fluid causes a lifting movement in which a head of the rolling diaphragm is linearly displaced.
• the volume compensation element comprises a compensation housing that is at least partially filled with a gas, in particular air
• the compensation housing has an outlet opening through which the hydraulic fluid flows into the volume compensation element under compression of the gas when the fluid temperature increases and flows out of the volume compensation element under expansion of the gas when the fluid temperature decreases
• the hydraulic fluid expands and flows into the volume compensation element.
• the rolling diaphragm then performs a reciprocating movement caused by the flowing hydraulic fluid. During this movement, the head of the rolling diaphragm is linearly displaced by rolling the diaphragm, thus compressing the gas. This releases additional volume for the hydraulic fluid, preventing the pressure in the drive from increasing.
• the drive according to the invention therefore enables pressure equalization over a large temperature range without free air in the drive and thus without disturbance of the hydraulic functions, since the gas is held enclosed by the rolling diaphragm in the compensation housing and hermetically separated from the hydraulic fluid.
• the outlet can act as a throttle, limiting the flow rate of the hydraulic fluid through it. This limits the impact of sudden pressure increases, such as those that can occur when the impeller moves within the actuator, on the rolling diaphragm. Conversely, slow, temperature-related volume changes of the hydraulic fluid generate a flow rate that can pass through the outlet unimpeded. Consequently, the outlet does not significantly affect the hydraulic function during actuator operation, despite the inherent volume compensation capability. It also limits the pressures acting on the rolling diaphragm, resulting in a long service life for the actuator.
• a rolling diaphragm since a rolling diaphragm is provided according to the invention, it does not experience any significant stretching due to the reciprocating movement of the rolling diaphragm, as the rolling diaphragm is only subjected to minimal stress due to the rolling action, thereby increasing the reliability and operational safety of the drive. In contrast, with stretching, for example similar to that of a balloon, the material stresses would be significantly higher, and thus the reliability and operational safety would be reduced.
• the volume compensation element according to the invention is characterized by a simple design and easy assembly due to its construction, which ultimately also simplifies the design and assembly of the drive according to the invention for realizing the volume compensation.
• the compensating housing includes a closure element with a flow-dependent check valve that closes the outlet when the back pressure of the hydraulic fluid outside the compensating element exceeds a predetermined value, thus preventing hydraulic fluid from flowing into the compensating element.
• the back pressure depends primarily on the flow velocity of the hydraulic fluid.
• the flow-dependent check valve closes the outlet when the back pressure of the hydraulic fluid outside the compensating element exceeds the predetermined value—which is determined primarily by the back pressures occurring during actuator operation—sudden pressure increases, such as those that can occur when the impeller moves within the actuator, cannot affect the rolling diaphragm.
• the rolling diaphragm comprises an inner surface which at least partially contacts the gas and an outer surface which at least partially rests against the inner wall of the compensation housing, and is designed such that a rolling area of the diaphragm rolls along the inner wall during the stroke movement, forming a rolling fold with either the outer or the inner surface. Accordingly, the rolling behavior of the two designs differs, with each enabling controlled rolling and thus increasing the reliability of the drive.
• the rolling diaphragm at the head has a greater material thickness than the walking area.
• This reinforcement improves force transmission into the rolling diaphragm and prevents deformation. This prevents certain areas, especially in the head, and thus improves the controlled rolling of the rolling membrane.
• a support element can be provided within the compensation housing, which is rigidly connected to the head, in particular wherein the support element is linearly displaceable against the compensation housing.
• the support element assists the controlled rolling of the diaphragm, and in particular, the linearly displaceable support element improves the controlled rolling by guiding the diaphragm.
• the support element provides reinforcement with the advantages described above.
• the rolling diaphragm includes a sealing ring with which it is attached to the compensation housing, particularly by injection molding. This increases the reliability of the volume compensation element and simplifies its manufacturing. Furthermore, it allows pressure equalization even under particularly large temperature fluctuations.
• the compensating housing comprises a first housing shell and a second housing shell, which are connected to each other at a joint such that the hydraulic fluid cannot penetrate the compensating housing at the joint.
• the shell design simplifies the manufacturing of the volume compensation element, such as the provision of the rolling diaphragm.
• the first housing shell can have a first sealing surface and the second housing shell a second sealing surface, with the sealing ring of the rolling diaphragm being clamped between the first and second sealing surfaces.
• the rolling membrane consists of a thermoplastic elastomer, most preferably a thermoplastic polyurethane.
• a thermoplastic elastomer most preferably a thermoplastic polyurethane.
• the rolling membrane can be made of a rubber elastomer, which, due to its material properties, allows for even greater functional reliability.
• a fabric can be incorporated into the membrane. This increases its robustness and reduces its elasticity, thereby also increasing functional reliability and improving controlled unwinding.
• the amount of hydraulic fluid is measured such that at a hydraulic fluid temperature corresponding to a predefined temperature, in particular 20°C, the gas within the hydraulic fluid is partially compressed.
• a predefined temperature in particular 20°C
• the gas within the hydraulic fluid is partially compressed.
• an increased quantity of hydraulic fluid, or hydraulic fluid cooled below the predefined temperature can be incorporated into the actuator housing. This ensures that the gas is partially compressed, i.e., pre-pressurized, at a fluid temperature corresponding to the predefined temperature.
• the volume of the hydraulic fluid decreases, allowing the hydraulic fluid to flow out of the volume compensation element as the gas expands, without creating a vacuum within the actuator. If a vacuum were to occur in the actuator, dissolved gases in the hydraulic fluid could be expelled, potentially disrupting or even causing the hydraulic damping functions to fail.
• the advantageous gas pre-charge prevents this, thus ensuring particularly reliable actuator operation across a wide temperature range, especially at low temperatures.
• the predefined temperature corresponds, for example, to the usual room temperature at the operating location of the drive.
• the flow-dependent check valve comprises a sealing point and a locking element by means of which the sealing point can be sealed, wherein a pressure force dependent on the back pressure acts on the locking element and the The locking element is subjected to a counterforce opposing the pressure force, such that if the back pressure is below the specified value, the locking element does not seal the sealing point, thus preventing the flow-dependent check valve from closing the outlet. Conversely, if the back pressure is above the specified value, the locking element seals the sealing point, thus preventing the flow-dependent check valve from closing the outlet.
• the counterforce prevents the locking element from sealing the sealing point. This allows for a particularly simple technical implementation of the flow-dependent check valve's operation. The counterforce thus ensures that the locking element does not seal the sealing point when the back pressure is below the specified value.
• the locking element can be designed as a geometric body, in particular a sphere or a cone, which can be displaced from a rest position (in which the geometric body does not seal the sealing point) by the back pressure.
• a separately designed return spring can be provided, which acts on the geometric body, with the spring force of the return spring providing the counterforce.
• the return spring ensures that the flow-dependent check valve is in a controlled open state in every position of the actuator – provided the back pressure is below the specified value – thereby increasing the operational reliability of the actuator.
• the flow-dependent check valve could also be designed without the return spring, in which case the counterforce could be provided, for example, primarily by the weight force acting on the locking element.
• the closure element can have a first chamber in which the geometric body is received, a second chamber into which the The valve has an outlet opening in which the return spring is located, and a tapered section through which the first chamber narrows towards the second chamber.
• the sealing point in particular as a circular sealing edge, is formed at the tapered section and that the geometric body is received in the first chamber in such a way that the geometric body is spaced away from the sealing point in its rest position, whereby the geometric body is moved into an end position when the dynamic pressure exceeds the specified value, in which the geometric body seals the sealing point.
• the locking element can alternatively or additionally be designed as an elongated, particularly tongue-shaped, elastically bendable flat part, especially made of spring steel or elastic plastic, which, from a resting state in which the flat part does not seal the sealing point, can be elastically bent by the back pressure, with the restoring force of the flat part providing the counterforce. This results in a particularly simple and durable design of the flow-dependent check valve.
• the sealing point surrounds the outflow opening in a flat manner, in particular as an annular projection, and that the flat part is attached to the closure element with a first section in such a way that a second section of the flat part faces the sealing point in the rest state.
• the two sections are spaced apart, with the flat section bending into a final state when the back pressure exceeds a specified value, such that the second section seals the sealing point.
• the locking element can alternatively or additionally be designed as a sensor with a sliding section, wherein the sliding section is inserted into the outflow opening and guided axially within it, thus allowing the sensor to be axially displaceable on the closure element. This allows for a particularly simple manufacture of the flow-dependent check valve.
• elastic spring arms whose free ends rest against the sealing element, are formed on the sensor. From a rest position, in which the sensor does not seal the sealing point, the sensor can be displaced by the back pressure, causing the spring arms to bend. The restoring force of the spring arms provides the counterforce. This results in a particularly simple and durable design for the flow-dependent check valve.
• the senor may be designed to have an elastic sealing element, in particular an O-ring, whereby, at a back pressure exceeding the specified value, the sensor is moved into an end position in which the elastic sealing element rests flat against the closure element, thus sealing the sealing point.
• the contact surface of the closure element, against which the elastic sealing element rests for sealing forms the sealing point. Since the flow-dependent check valve has a flat sealing surface and not merely a sealing edge, this design is particularly robust and wear-resistant. Furthermore, contamination in the The sealing area is covered by the elastic sealing element, thus maintaining the sealing function even if the sealing point is dirty.
• the drive is advantageously designed such that the drive mechanism comprises an output shaft rotatably mounted about a pivot axis, a linearly displaceable piston coupled to the output shaft which rotates the output shaft upon displacement, and a compression spring with a first end and a second end, the first end of which rests against the piston and exerts a compression spring force on it.
• the drive mechanism additionally comprises a spindle with a spindle plate against which the second end of the compression spring rests and via which the compression spring force can be adjusted.
• the volume compensation element is arranged in a space enclosed by the compression spring and/or within the spindle and/or is at least partially formed by the spindle. This enables a particularly simple and compact design of the drive.
• FIG. 1 shows a first embodiment of a drive 11 according to the invention, comprising a drive mechanism 13 arranged at least partially in a drive housing 15 and a volume compensation element 19.
• the drive mechanism 13 includes an output shaft 77 rotatably mounted about a pivot axis, a linearly displaceable piston 79 coupled to the output shaft 77, which rotates the output shaft 77 when displaced, and a compression spring 81.
• the compression spring 81 has a first end 83 and a second end 85, wherein the first end 83 of the compression spring 81 bears against the piston 79 and exerts a compression spring force on it.
• a spindle 87 with a spindle plate 89 is provided, against which the second end 85 of the compression spring 81 bears and via which spindle 87 the compression spring force can be adjusted.
• a hydraulic fluid 17 in the form of oil is contained within the drive housing 15.
• a chamber 91 is enclosed by the compression spring 81. This chamber 91 is also filled with the oil 17, and the volume compensation element 19 is located within it.
• the volume compensation element 19 compensates for volume changes of the oil 17 due to temperature variations, particularly those caused by climatic conditions, thereby maintaining a constant pressure within the drive 11.
• Fig. 2 shows the volume compensation element 19 from Fig. 1 in two different states, with the constructive structure first being explained using the illustration above.
• the volume compensation element 19 comprises a compensation housing 23 with a first housing shell 23a and a second housing shell 23b, which is partially filled with a gas 20 in the form of air.
• the rolling diaphragm 21 has a sealing ring 34, with which the rolling diaphragm 21 is injection-molded onto the compensation housing 23, in particular the second housing shell 23b.
• the rolling diaphragm 21 also has a head 30, which can also be referred to as the diaphragm base or base, and a flexing area 31, wherein the rolling diaphragm 21 has a material thickness at the head 30 that is greater than that of the flexing area 31.
• the rolling diaphragm 21 comprises an inner surface 21a, which contacts the air 20, and an outer surface 21b, with which the rolling diaphragm 21 rests against the inner wall of the expansion housing 23, in particular the second housing shell 23b.
• the first housing shell 23a and the second housing shell 23b are connected to each other at a joint 75, for example by welding, such that the oil 17 cannot penetrate the expansion housing 23 at the joint 75.
• the first housing shell 23a also has a first sealing surface 35 and the second housing shell 23b has a second sealing surface 36 at the joint 75, with the sealing ring 34 of the rolling diaphragm 21 being clamped between the first sealing surface 35 and the second sealing surface 36.
• the expansion housing 23, in particular the second housing shell 23b, has a drain opening 27 through which the oil 17 can generally flow.
• the air 20, however, is held enclosed by the rolling diaphragm 21 in the expansion housing 23 and is hermetically separated from the oil 17.
• FIG. 2 The upper representation in Fig. 2 The volume compensation element 19 is shown in a state in which no oil 17 has yet flowed into the volume compensation element 19 through the outflow opening 27.
• the volume compensation element 19 is shown in a state in which the oil 17, upon an increase in fluid temperature, flows into the volume compensation element 19 through the outflow opening 27, expanding as it does so.
• the rolling diaphragm 21 performs a stroke caused by the flowing oil 17, during which the head 30 of the rolling diaphragm 21 is displaced linearly to the right in the illustration.
• the volume of the air 20 held by the rolling diaphragm 21 in the compensation housing 23 decreases during this stroke.
• the oil flows into... Fig. 2
• the oil 17 flows through the outlet opening 27 into the volume compensation element 19 under compression of the air 20. Due to the stroke movement of the rolling diaphragm 21, an additional volume corresponding to the expansion of the oil 17 as the temperature increases is released, so that the pressure in the drive 11 does not rise.
• the rolling diaphragm 21 performs a reciprocating movement, during which the head 30 of the rolling diaphragm 21 is shown in the lower illustration. Fig. 2 The position is shifted linearly to the left.
• the oil 17 flows out of the volume compensation element 19 through the outflow opening 27, accompanied by the expansion of the air 20.
• the rolling area 31 of the rolling diaphragm 21 rolls along the inner wall of the compensating housing 23, in particular the second housing shell 23b, forming a roll fold 33.
• the rolling diaphragm 21 does not experience any significant stretching due to the lifting movement of the rolling diaphragm 21, since The rolling membrane 21 is subjected to only minimal stress due to its rolling action, thereby increasing the reliability and operational safety of the drive 11.
• the rolling membrane 21 is designed for controlled rolling, in particular by its flexing area and the correspondingly increased material thickness of the head 30. Other methods of reinforcing the head 30, such as an incorporated fabric or a support element, are also conceivable.
• the rolling diaphragm 21 performs a stroke movement due to the typically high temperatures of a fire, exceeding a normal working stroke, for example, due to solar radiation. In this way, an additional volume can be provided for the expanding oil 17 in the event of a fire, enabling the actuator 11 to withstand such high temperatures without leakage.
• FIG. 3 The volume compensation element 19 of a second embodiment of a drive 11 according to the invention is shown, wherein, in contrast to the volume compensation element 19, it is made of Fig. 2 A rolling area 31 of the rolling diaphragm 21 rolls during a lifting movement, forming a rolling fold 33 with an inner surface 21a of the rolling diaphragm 21 against an inner wall of the compensating housing 23, in particular the first housing shell 23a.
• Fig. 3 Here, two states are simultaneously depicted: a state in which no hydraulic fluid 17 flows into the volume compensation element 19, and a state in which the rolling diaphragm 21 performs a stroke movement caused by the flowing hydraulic fluid 17, in which the head 30 of the rolling diaphragm 21 is shown in the illustration according to Fig. 3 is shifted linearly to the right.
• FIG. 4 The volume compensation element 19 of a third embodiment of a drive 11 according to the invention is shown, in which, in contrast to the volume compensation element 19, Fig. 3 A support element 93 is provided which is firmly connected, for example by bonding, to the head 30 of the rolling membrane 21. How in Fig. 3 are also in Fig. 4 Two states of the volume compensation element 19 are shown simultaneously. Since the support element 93 facilitates controlled rolling of the rolling membrane 21, the rolling membrane 21 does not have an increased material thickness at the head 30 compared to the material thickness of a flex area 31 of the rolling membrane 21. In addition, the support element 93 can be linearly displaceable on the compensation housing 23, which in Fig. 4 However, it is not shown.
• FIG. 5 Figure 1 shows the volume compensation element 19 of a fourth embodiment of a drive 11 according to the invention, which is in the same state as the volume compensation element 19 of the lower illustration.
• Fig. 2 The rolling membrane 21 of the volume compensation element 19 is also located there.
• Fig. 5 The assembly comprises a sealing ring 34 which is clamped at a connection point 75 between a first sealing surface 35 of a first housing shell 23a and a second sealing surface 36 of a second housing shell 23b.
• the rolling diaphragm 21 unlike the one in Fig. 2 shown rolling membrane 21 made of a rubber elastomer, wherein in addition a Fig. 5 Tissue not shown is incorporated into the rolling membrane 21.
• FIG. 6 Figure 1 shows the volume compensation element 19 of a fifth embodiment of a drive 11 according to the invention, in which the gas 20 is already partially compressed at a predefined temperature of 20 °C.
• the hydraulic fluid 17 with a fluid temperature of, for example, 10 °C was included in the drive housing 15.
• the hydraulic fluid 17 was heated to the predefined temperature of 20 °C, it expanded such that the gas 20 was partially compressed or pre-tensioned as a result of a stroke movement of the rolling diaphragm 21.
• the volume of the hydraulic fluid 17 decreases accordingly, with the hydraulic fluid 17 expanding as the gas 20 expands through the The gas can flow out of the discharge opening 27 from the volume compensation element 19 without creating a vacuum in the actuator 11. If a vacuum were to occur in the actuator 11, dissolved gases in the hydraulic fluid 17 could be expelled, potentially disrupting or even causing the hydraulic damping functions to fail.
• the advantageous pre-charge of the gas 20 prevents this, thus ensuring particularly reliable operation of the actuator 11 over a wide temperature range, especially at low temperatures.
• the volume compensation element 19 is designed so that the compensation housing 23 includes a closure element 25 which incorporates a flow-dependent check valve 29.
• the flow-dependent check valve 29 closes the outlet opening 27 when the back pressure of the hydraulic fluid 17 occurring outside the volume compensation element 19 exceeds a predetermined value, preventing hydraulic fluid 17 from flowing into the volume compensation element 19.
• the predetermined value depends on the operating pressures, in particular the back pressures occurring at the flow-dependent check valve 29 during operation.
• the back pressure is in particular depends on the flow velocity of the hydraulic fluid 17, whereby the dynamic pressure increases with the flow velocity.
• Fig. 7 This relates to a sixth embodiment of a drive 11 according to the invention, the compensating housing 23 of which comprises a closure element 25 with a flow-dependent check valve 29, wherein only a detailed view of the closure element 25 with the flow-dependent check valve 29 is shown.
• the closure element 25 has a first chamber 65, a second chamber 67 into which the outflow opening 27 opens, and a tapered section 69, via which the first chamber 65 tapers to the second chamber 67.
• a geometric body 47 in the form of a sphere 47a is accommodated, which is acted upon by a return spring 63, which is arranged in the second chamber 67.
• a circular sealing edge 39 is formed on the tapered section 69, which can be sealed by the sphere 47a and thus forms a sealing point.
• the left-hand representation in Fig. 7 The flow-dependent check valve 29 is shown in an open position, in which the flow-dependent check valve 29 does not close the outlet opening 27.
• the ball 47a is in a rest position, in which the ball 47a is spaced from the sealing edge 39 and does not seal against the sealing edge 39. At low flow velocities, the hydraulic fluid 17 can thus flow past the ball 47a and through the outlet opening 27 into the volume compensation element 19.
• a back pressure builds up on the ball 47a, which depends in particular on the flow velocity of the hydraulic fluid 17. Due to the back pressure, a pressure force acts on the ball 47a, which attempts to displace the ball 47a towards the sealing edge 39. Conversely, the ball 47a is subjected to a counterforce provided by the spring force of the return spring 63.
• the ball 47a can be displaced from its rest position, compressing the return spring 63.
• the pressure force is so high compared to the spring force of the return spring 63 that the ball 47a is moved into an end position, which is shown in the right-hand illustration. Fig. 7 As shown, the ball 47a seals the sealing edge 39, causing the flow-dependent check valve 29 to close the outlet 27.
• the pressure force falls below the spring force of the return spring 63, the ball 47a can be moved back by the spring force of the return spring 63. The ball 47a is then again spaced away from the sealing edge 39, preventing the flow-dependent check valve 29 from closing the outlet 27.
• the specified value is predetermined, and in particular the return spring 63 is dimensioned according to this predetermined value, such that operational back pressures move the ball 47a into its end position. However, temperature-related volume changes of the hydraulic fluid 17 result in no or only negligible back pressures.
• Fig. 8 This relates to a seventh embodiment of a drive 11 according to the invention, the compensating housing 23 of which comprises an alternative closure element 25 with a flow-dependent check valve 29, wherein only a detailed view of the closure element 25 with the flow-dependent check valve 29 is shown.
• the operation of the flow-dependent check valve 29 is analogous to that described above.
• Fig. 7 The described function also applies to the locking element 25 as described.
• Fig. 8 in particular it has a first chamber 65, a second chamber 67 and a tapering section 69, above which the first chamber 65 tapers to the second chamber 67, wherein the outflow opening 27 opens into the second chamber 67 transversely to the direction of the tapering.
• Fig. 9 This relates to an eighth embodiment of a drive 11 according to the invention, the compensating housing 23 of which comprises an alternative closure element 25 with a flow-dependent check valve 29, wherein only a detailed view of the closure element 25 with the flow-dependent check valve 29 is shown.
• the closure element 25 has a tongue-shaped, elastically bendable flat part 49 made of spring steel, which is attached to the closure element 25 by a first section 51.
• the sealing point in the form of an annular projection 41 surrounding the outflow opening 27 is provided on the closure element 25, which can be sealed by a second section 53 of the flat part 49.
• FIG. 9 Figure 1 shows the flow-dependent check valve 29 in an open state, in which the flow-dependent check valve 29 does not close the outlet opening 27.
• the flat part 49 is in a resting state, in which the second section 53 is spaced apart from the projection 41 and does not seal the projection 41. Accordingly, at low flow velocities, the hydraulic fluid 17 can flow past the flat part 49 and through the outlet opening 27 into the volume compensation element 19.
• a dynamic pressure builds up on the flat part 49, which depends in particular on the flow velocity of the hydraulic fluid 17. Due to this dynamic pressure, a pressure force acts on the flat part 49, which attempts to bend the flat part 49, especially with regard to the second section 53, towards the projection 41.
• the flat part 49 is subjected to a counterforce provided by the restoring force of the flat part 49. If the compressive force exceeds the restoring force of the flat part 49, the flat part 49 can be elastically bent from its resting state.
• the compressive force is so high compared to the restoring force of the flat part 49 that the flat part 49 is bent into a final state, which is shown in the right-hand illustration.
• Fig. 9 As shown, the second section 53 seals the projection 41, causing the flow-dependent check valve 29 to close the outlet 27. If the pressure force decreases below the restoring force of the flat part 49, the flat part 49 can return to its original position, so that the second section 53 is spaced away from the projection 41, thus preventing the flow-dependent check valve 29 from closing the outlet 27.
• the specified value is predetermined, and in particular the flat part 49 is dimensioned according to this predetermined value, such that operational back pressures bend the flat part 49 into its final state. However, temperature-related volume changes of the hydraulic fluid 17 result in no or only negligible back pressures.
• Fig. 10 This shows in Fig. 9
• the illustrated closure element 25 with the flow-dependent check valve 29 is shown in a perspective detail view, in which in particular the projection 41 as well as the tongue-shaped design and the attachment of the flat part 49 to the closure element 25 are shown.
• Fig. 11 This relates to a ninth embodiment of a drive 11 according to the invention, the compensating housing 23 of which comprises an alternative closure element 25 with a flow-dependent check valve 29. Again, only a detailed view of the closure element 25 with the flow-dependent check valve 29 is shown.
• the closure element 25 has a sensor 55 with a sliding section 57, the sliding section 57 being inserted into the outflow opening 27 and guided axially displaceably therein. Consequently, the sensor 55 is also arranged axially displaceably on the closure element 25.
• locking lugs are formed on the sliding section 57 to prevent unintentional slippage of the sliding section 57 from the outflow opening 27.
• the receiver 55 has two elastic spring arms 59, the free ends 61 of which each bear against the closure element 25. Furthermore, the receiver 55 has an elastic sealing element 71 in the form of an O-ring, and the closure element 25 has a contact surface 43 provided for the sealing element 71, which can be sealed by the sealing element 71 and forms the sealing point.
• FIG. 11 Figure 1 shows the flow-dependent check valve 29 in an open position, in which the flow-dependent check valve 29 does not close the outlet opening 27.
• the sensor 55 is in a rest position, in which the sealing element 71 is spaced away from the contact surface 43 and does not seal the contact surface 43. Accordingly, at low flow velocities, the hydraulic fluid 17 can flow past the sealing element 71 and through the outlet opening 27 into the volume compensation element 19. This creates a back pressure on the sensor 55, which depends in particular on the flow velocity of the hydraulic fluid 17. Due to this back pressure, a compressive force acts on the sensor 55, which attempts to move the sensor 55 with the sealing element 71 towards the contact surface 43, thereby bending the spring arms 59. In contrast, the sensor 55 is subjected to a counterforce provided by the restoring force of the spring arms 59. If the compressive force exceeds the restoring force of the spring arms 59, the sensor 55 can be moved from its rest position.
• the sealing element 71 seals the contact surface 43, causing the flow-dependent check valve 29 to close the outflow opening 27. If the pressure force decreases below the restoring force of the spring arms 59, the receiver 55 can be moved back by the restoring force of the spring arms 59.
• the sealing element 71 is positioned so that it is spaced away from the contact surface 43, preventing the flow-dependent check valve 29 from closing the outlet opening 27.
• the specified value is predetermined, and in particular the spring arms 59 are dimensioned according to this predetermined value, such that operational back pressures move the sensor 55 into its end position.
• temperature-related volume changes of the hydraulic fluid 17 result in no or only negligible back pressures.
• Fig. 12 This shows in Fig. 11
• the illustrated closure element 25 with the flow-dependent check valve 29 is shown in a perspective detail view, in which in particular the receiver 55 with the sealing element 71 and the design of the spring arms 59 are shown.

Landscapes

• Check Valves (AREA)
• Reciprocating Pumps (AREA)

Priority Applications (1)

Applications Claiming Priority (1)

Publications (3)

Family

ID=92539015

Family Applications (1)

Country Status (4)

Family Cites Families (4)

• 2023
  • 2023-09-04 DE DE102023208503.8A patent/DE102023208503B4/de active Active
• 2024
  • 2024-08-22 EP EP24195860.2A patent/EP4517036B1/de active Active
  • 2024-08-22 RS RS20260422A patent/RS67955B1/sr unknown
  • 2024-08-22 PL PL24195860.2T patent/PL4517036T3/pl unknown

Also Published As

Similar Documents

Legal Events