EP3366164B1 - Kühlschrank mit einer oder mehreren automatisch schliessenden türen - Google Patents

Kühlschrank mit einer oder mehreren automatisch schliessenden türen Download PDF

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Publication number
EP3366164B1
EP3366164B1 EP18158693.4A EP18158693A EP3366164B1 EP 3366164 B1 EP3366164 B1 EP 3366164B1 EP 18158693 A EP18158693 A EP 18158693A EP 3366164 B1 EP3366164 B1 EP 3366164B1
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EP
European Patent Office
Prior art keywords
door
piston
frame
angular
rotation axis
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English (en)
French (fr)
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EP3366164A1 (de
Inventor
Nicola BOSCHI
Paolo TORMEN
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Epta SpA
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Epta SpA
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Classifications

    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47F—SPECIAL FURNITURE, FITTINGS, OR ACCESSORIES FOR SHOPS, STOREHOUSES, BARS, RESTAURANTS OR THE LIKE; PAYING COUNTERS
    • A47F3/00—Show cases or show cabinets
    • A47F3/04—Show cases or show cabinets air-conditioned, refrigerated
    • A47F3/0404—Cases or cabinets of the closed type
    • A47F3/0426—Details
    • A47F3/043—Doors, covers
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D11/00—Additional features or accessories of hinges
    • E05D11/06—Devices for limiting the opening movement of hinges
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D7/00—Hinges or pivots of special construction
    • E05D7/08—Hinges or pivots of special construction for use in suspensions comprising two spigots placed at opposite edges of the wing, especially at the top and the bottom, e.g. trunnions
    • E05D7/081—Hinges or pivots of special construction for use in suspensions comprising two spigots placed at opposite edges of the wing, especially at the top and the bottom, e.g. trunnions the pivot axis of the wing being situated near one edge of the wing, especially at the top and bottom, e.g. trunnions
    • 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
    • E05F1/00—Closers or openers for wings, not otherwise provided for in this subclass
    • E05F1/08—Closers or openers for wings, not otherwise provided for in this subclass spring-actuated, e.g. for horizontally sliding wings
    • E05F1/10—Closers or openers for wings, not otherwise provided for in this subclass spring-actuated, e.g. for horizontally sliding wings for swinging wings, e.g. counterbalance
    • E05F1/1091—Closers or openers for wings, not otherwise provided for in this subclass spring-actuated, e.g. for horizontally sliding wings for swinging wings, e.g. counterbalance with a gas spring
    • 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
    • E05F1/00—Closers or openers for wings, not otherwise provided for in this subclass
    • E05F1/08—Closers or openers for wings, not otherwise provided for in this subclass spring-actuated, e.g. for horizontally sliding wings
    • E05F1/10—Closers or openers for wings, not otherwise provided for in this subclass spring-actuated, e.g. for horizontally sliding wings for swinging wings, e.g. counterbalance
    • E05F1/12—Mechanisms in the shape of hinges or pivots, operated by springs
    • E05F1/1292—Mechanisms in the shape of hinges or pivots, operated by springs with a gas spring
    • 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
    • E05F3/22—Additional arrangements for closers, e.g. for holding the wing in opened or other position
    • E05F3/221—Mechanical power-locks, e.g. for holding the wing open or for free-moving zones
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/02—Doors; Covers
    • F25D23/028—Details
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME RELATING TO HINGES OR OTHER SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS AND DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION, CHECKS FOR WINGS AND WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/30—Application of doors, windows, wings or fittings thereof for domestic appliances
    • E05Y2900/306—Application of doors, windows, wings or fittings thereof for domestic appliances for freezers
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05Y—INDEXING SCHEME RELATING TO HINGES OR OTHER SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS AND DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION, CHECKS FOR WINGS AND WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05Y2900/00—Application of doors, windows, wings or fittings thereof
    • E05Y2900/30—Application of doors, windows, wings or fittings thereof for domestic appliances
    • E05Y2900/31—Application of doors, windows, wings or fittings thereof for domestic appliances for refrigerators

Definitions

  • the object of the present invention is a refrigerated cabinet with one or more automatically closing doors.
  • Such refrigerated cabinet may be vertical, semi-vertical or combined, and may be at a negative or positive temperature.
  • the doors for freezer cabinets and refrigerated cabinets used in the commercial refrigeration field have an automatic closing system based on torsion springs.
  • Such springs are loaded by opening the door and release their potential elastic energy during the closing movement of the same door. Since such systems are based on elastic energy, the force with which the door closes responds in principle to Hooke's law. Therefore, the greater the angle at which the door is opened, the greater the force that will tend to close it. In closing, the elastic force that is generated tends to accelerate the door against the support (frame) of the cabinet causing an impact that causes noise, vibrations, and sometimes even causes the adjacent doors to open.
  • devices that keep the door open at about 90° are used.
  • the latter may be either springs shaped to fit in specially provided abutments with an intentional action of the operator in loading the cabinet or snap systems that are activated by forcing the door over ninety degrees.
  • the desired functions of automatic closing and of stopping the door therefore require the use of at least two devices.
  • the hydraulic system varies its effective response according to the position in which it is installed. A calibration stage is therefore required.
  • the viscosity of the oil is affected by the temperature at which it operates and an installation inside the cabinet requires different contrivances than an external installation.
  • JPH06263186 A discloses a refrigerated cabinet with an automatically closing door.
  • the object of the present invention is to eliminate the drawbacks of the prior art described above, providing a refrigerated cabinet with one or more automatically closing doors that do not generate impacts between the door and frame while minimizing the closing time of the same door.
  • a further object of the present invention is to provide a refrigerated cabinet with one or more automatically closing doors that allow the door stop in a defined open position without the use of additional door stop devices with respect to the door's automatic closing system.
  • a further object of the present invention is to provide a refrigerated cabinet with one or more automatically closing doors that is simple and economical to make.
  • a refrigerated cabinet with one or more automatically closing doors is indicated collectively with 1.
  • Such refrigerated cabinet may be vertical, semi-vertical or combined, and may be at a negative or positive temperature.
  • the refrigerated cabinet 1 comprises a support frame 2, which defines a load compartment 3, and at least one door 10 for closing such load compartment 3.
  • the frame 2 defines the support structure of the cabinet 1 and comprises a support base 2a, a plurality of side walls 2b (including a back wall) and a top 2c, which defines the top of the cabinet 1.
  • Load compartment means, in particular, the volume inside the structure of the refrigerated cabinet that is intended for displaying and storing the goods for sale.
  • the door 10 is associated with the frame 2 by hinging means 20, 30 which define a vertical rotation axis X about which the door 10 may rotate to move between a closed position and a predefined position of maximum opening.
  • the door 10 is a vertical-type door.
  • the refrigerated cabinet 1 comprises an automatic closing system of the aforesaid at least one door 10.
  • the refrigerated cabinet 1 may comprise a single door 10, or two or more doors 10, as illustrated in Figures 1 and 2 .
  • each of these doors 10 is provided with an automatic closing system.
  • the door 10 is glazed. However, embodiments may be foreseen wherein the door 10 is not glazed.
  • the aforesaid hinging means comprise an upper hinge 20, which is fixed to the top 2c of the frame 2 of the cabinet 1 and a lower hinge 3, which is fixed to the base 2a of the frame 2.
  • the upper hinge 20 and the lower hinge 30 are vertically aligned with each other and define the aforesaid rotation axis X.
  • the hinges 20, 30 are made of materials with a low friction coefficient and self-lubricating to reduce both mutual wear and the need for maintenance and periodic greasing.
  • the automatic closure system of the door 10 comprises a hydropneumatic piston 40 which is hinged - at its opposite two ends 40a and 40b along its own dynamic action axis Y - respectively to the frame 2 and to the door 10.
  • the two hinging points 40a and 40b of the piston 40 to the frame 2 and to the door 10 are substantially at the same vertical height, so as to make the piston 30 work on a substantially horizontal plane.
  • the force generated by the piston 40 does not have a substantially vertical component, which would need to be compensated, for example, by means of thrust bearings, with an increase in costs and in constructive complexity.
  • Such configuration also makes it possible to reduce the overall dimensions with respect to a configuration with hinging at different heights.
  • Such hinging defines for the piston 40 a rotationally free connection at both ends about the respective connecting pins.
  • the hydropneumatic piston 40 can therefore follow the door 10 in rotation. This causes a progressive variation of both the spatial orientation of the piston 40 with respect to the frame 2 and to the door 10, and of the length extension of the piston 40 along its dynamic action axis Y.
  • the variation in length extension of the piston (compression or extension) dynamically activates the piston itself.
  • hydropneumatic piston is a device well known to a person skilled in the art and will not therefore be described here in detail, but rather only some general information will be provided.
  • a hydropneumatic piston is a device consisting of two mechanical parts.
  • a first part consists of a hollow cylinder, which is filled with a fluid and inside of which slides a movable part, called stem.
  • the stem At the end of the stem placed within the cylinder the stem has a head with dimensions corresponding to the inner section of the cylinder and which divides the cylinder into two variable volume chambers. The movement of the head of the stem inside the cylinder is controlled by the pressure difference between the two chambers.
  • a hydropneumatic piston uses both gas and oil as the internal fluid. This introduces a viscous damping in the movement of the stem within the cylinder.
  • a hydropneumatic piston is provided at its two ends 40a and 40b with couplings functional for connecting to the mobile component to be controlled (in this case, the door 10) and to the fixed reference component (in this case, the frame 2).
  • the hydropneumatic piston is provided at its first end 40a with a ball joint coupling and at its second end 40b with a forked coupling.
  • the ball joint is used to compensate for horizontal misalignments resulting from the global installation tolerances of the cabinet.
  • a hydropneumatic piston is a linear actuator able to generate a force F along the longitudinal extension axis of the piston, defined hereinafter as the dynamic action axis Y.
  • Such force F may be generated by the piston as a response to both a compression and an extension thereof.
  • the hydropneumatic pistons unlike mechanical springs, have a curve representative of the force F returned in extension (i.e., following their compression) which is very flat, almost linear, as a function of the stroke of the piston.
  • a hydropneumatic piston 40 when compressed, a hydropneumatic piston 40 generates a substantially constant force F (of extension) as a function of the degree of compression of the piston.
  • the ratio between the force F (of extension) generated in the initial phase of compression and the force F (of extension) generated in the final phase of compression is between 1.2 and 1.4.
  • a hydropneumatic piston generates, as a result of compression, a substantially constant force F (of extension) as a function of the degree of compression of the piston is functional for solving the problem underlying the present invention.
  • the aforesaid hydropneumatic piston 40 of the automatic closing system of the door 10 is hinged to the door 10 in an offset position with respect to the rotation axis X through a lever extension 43 which is integral in rotation to the same door 10.
  • the offset with respect to the rotation axis X defines an arm B for the force F exerted by the piston 40 on the door 10.
  • the door 10 is therefore subjected to an angular momentum M about the rotation axis X.
  • the hydropneumatic piston 40 follows in rotation the door 10 by varying its own orientation with respect to the frame 2 and the same door. Therefore, during the opening/closing movement of the door 10, the dynamic action axis Y of the piston 40 changes its orientation relative to the rotation axis X, with consequent variation also of the arm B of the force F, as may be seen in Figures 3, 4 and 5 .
  • the arm B is, in fact, defined by the perpendicular distance between the aforementioned action axis Y and the rotation axis X.
  • the value of the angular momentum M therefore varies substantially only according to the value of the arm B of the force F.
  • the two hinging points of the hydropneumatic piston 40 on the frame 2 and on the lever extension 43 are positioned with respect to the rotation axis X so that:
  • the door 10 once opened and left to the sole action of the hydropneumatic piston 40, will be subjected to a closing angular momentum M about the rotation axis X increasing in value as the angle of opening decreases. If the door 10 is opened until the aforesaid predefined position of maximum opening is reached, the angular momentum M will instead be substantially zero and the door 10 will be automatically held still in equilibrium. The position of maximum opening therefore defines a door stop position.
  • the door stop in a predefined angular position of opening is obtained directly from the door closing system without the need to adopt devices intended to stop the door.
  • the automatic closing system of the door 10 is sized in such a way that the position of maximum opening, corresponding to the door stop position, is fixed at an angle close to 90°, preferably between 80-85°. At such angular values of opening, the door is almost completely open and the loading operations of the refrigerated cabinet 1 are thus facilitated.
  • the intensity of the stress applied to the door in closing (defined by the angular momentum M) reaches its maximum when the door is near the closed position, i.e. in the position wherein the closing stress is more functional to ensure a complete and effective closure of the door 10.
  • the two hinging points of the hydropneumatic piston 40 on the frame 2 and on the lever extension 43 are positioned with respect to the rotation axis X in such a way that even in the closed position said hydropneumatic piston 40 exerts a force F which via said lever extension 43 develops about the rotation axis X an angular momentum M which statically holds the door 10 closed.
  • the automatic closing system guarantees a complete and effective closing of the door 10.
  • the hydropneumatic piston 40 is hinged to the frame 2 at a top portion 2c of the cabinet 1, while the piston 40 is hinged to the door 10 by the aforesaid lever extension 43 at a top portion of the same door.
  • the two hinging points are substantially at the same height. In this way, the hydropneumatic piston 40 operates lying on a horizontal plane.
  • the hydropneumatic piston may be hinged to the frame 2 at a portion of the support base 2a of the cabinet 1, while the piston 41 is hinged to the door 10 by the aforesaid lever extension 43 at a base portion of the same door.
  • the two hinging points are substantially at the same height.
  • the hinging point 40a of the piston 40 on the frame 2 is in a rearward position towards the inside of the cabinet with respect to a vertical plane V defined by the door 10 in the closed position.
  • the rotation axis X lies on the vertical plane V.
  • the aforesaid lever extension 43 is sized such that the hinging point 40b of the piston 40 on the door 2 is always in a rearward position toward the inside of the cabinet with respect to the aforesaid vertical plane V, defined by the door 10 in the closed position, for any angular position assumed by the door between the closed position and the position of maximum opening (door stop). In this way it is ensured that between the angular operating positions of the door 10 there is always an arm B for applying force so as to cause an angular momentum M for closing the door.
  • the hydropneumatic piston 40 is positioned rearwardly of the door 10, i.e., at the portion of the frame 2 at which the door 10 closes.
  • the hydropneumatic piston 40 may be installed in such a way that it works in compression, i.e., it exerts its thrust in extension.
  • the two hinging points of the hydropneumatic piston 40 on the frame 2 and on the lever extension 43 are positioned relative to the rotation axis X so that the hydropneumatic piston 40 is always compressed in the opening movement of the door between the closed position and the position of maximum opening and always exerts a force F which is directed from the hinging point on the frame 2 toward the hinging point on the lever extension 43 along its dynamic action axis Y.
  • the hydropneumatic piston 4 is hinged to the frame 2 at the cylinder 41 and is hinged to the door 10 (via the lever extension 43) at the stem 42.
  • the hydropneumatic piston 4 is hinged to the frame 2 at the cylinder 41 and is hinged to the door 10 (via the lever extension 43) at the stem 42.
  • the lever extension 43 extends from the door 10 towards the inside of the cabinet 1. In this way, the extension 43 never protrudes with respect to the cabinet 1 but rather is always covered by the door 10.
  • the lever extension 43 is not made in one piece with the door frame, but rather consists of a profile fixed to the door by fixing means (such as rivets or screws).
  • the refrigerated cabinet 1 comprises mechanical limit stop means 50 suitable to define a limit stop for the door having an angular opening value not lower than that corresponding to said position of maximum opening.
  • These mechanical limit stop means 50 are suitable to prevent the door 10 from being forced in opening by stressing the hydropneumatic piston 40.
  • such means 50 are configured so as to define a limit stop for the door in an angular position corresponding to the aforesaid position of maximum opening (or door stop) or in such a way as to define a limit stop for the door in an upper angular position at the aforementioned position of maximum opening (or door stop), but which is within the operational limits of the hydropneumatic piston 40. It is essential that the angular position of limit stop defined by the aforementioned mechanical means 50 is not lower than that corresponding to the position of maximum opening (or door stop). In such case, in fact, the door would be prevented from reaching such position of equilibrium (wherein the angular momentum is substantially zero or in any case not sufficient to overcome the friction) and therefore the automatic closing system would be prevented from defining the door stop.
  • such mechanical limit stop means 50 are not suitable for holding the door in the maximum opening/door stop position (this function is performed by the closing system, as already described), but are instead suitable to prevent the door 10 from being forced to open beyond the operating limits of the hydropneumatic piston. In this way, it is avoided that, if (even accidentally) the door is forced beyond the aforesaid door stop position, the hydropneumatic piston 40 is subjected to movements and/or stresses outside its operating range. If the door is forced in opening, the stress will be supported by the mechanical limit stop means 50 and not by the hydropneumatic piston 40, thus preventing the piston from being damaged.
  • the aforesaid mechanical limit stop means 50 are positioned at the lower hinge 30 of the door.
  • the aforesaid mechanical limit stop means 50 comprise in particular:
  • the rotation movement of the door about the axis X causes a relative movement between the pin 54 and the slot 52, as shown in Figures 9a, 9b and 9c .
  • the two ends of the slot define two limit stops for the pin 54.
  • the slot 52 is dimensioned such that one of the two limit stops corresponds to the angular position of the position of maximum opening or to an upper angular position placed within the operating range of the piston 40. In this way, any mechanical stress resulting from an attempt to force the door to open would be releases from the first plate 51 on the pin 54 and then onto the frame 2 of the cabinet.
  • the cylinder 41 of the hydropneumatic piston 40 has at least two longitudinal portions with different internal cross-sections.
  • a first longitudinal portion 41a of the cylinder has a greater internal cross-section than the second longitudinal portion 41b. Due to such configuration, the head 45 of the stem 42 of the piston 40 at such first portion 41a meets a lower sliding resistance than that which it meets in the second portion 41b. Consequently, the head of the stem 42 of the piston 40 may slide faster when it passes into the first portion 41a with respect to when instead it passes into the second portion 42b.
  • the hydropneumatic piston 40 is oriented with respect to the rotation axis X in such a way that:
  • the closing speed of the door 10 is therefore differentiated as a function of the angular position of closure it assumes.
  • Such speed differentiation as a function of the angular position assumed by the door is exploited in such a way that:
  • the transition from the initial closing phase (faster) to the final closing phase (slower) may be sudden.
  • the aforesaid first predefined intermediate angular position i.e., where the faster, initial closing phase ends
  • coincides with the aforesaid second predefined intermediate angular position i.e. where the slower, final closing phase begins).
  • the passage between the two closing phases may be smooth, due to an intermediate closing phase, characterized by intermediate closing speeds, preferably decreasing progressively.
  • the cylinder 41 of the hydropneumatic piston 40 may comprise an intermediate longitudinal portion 41c which is comprised between the first 41a and the second longitudinal portion 41b.
  • Such intermediate longitudinal portion 41c has an internal connecting cross-section between the sections of said first portion 41a and said second portion 41b, such that, at the intermediate portion 41c, the head of the stem 42 of the piston 40 meets a sliding resistance intermediate with respect to that which it meets in said first portion 41a and that in said second portion 41b and thus slides therein at an intermediate speed.
  • the hydropneumatic piston 40 is oriented with respect to the rotation axis X such that the head of the stem 42 passes into said intermediate portion 41c when the door 10 moves in the angular range of opening comprised between the aforementioned first predefined intermediate angular position (i.e., where the faster initial closing phase ends) and the aforesaid second predefined intermediate angular position (i.e., where the slower final closing phase begins).
  • the initial (faster) closing phase covers an angular range from 80°-85° (maximum closed position) to 60°-50° (first intermediate position);
  • the intermediate closing phase (decreasing intermediate speed) covers an angular range of 60°-50° (first intermediate position) up to 15°-25° (second intermediate position);
  • the final closing phase covers the remaining angular range to the closed position, i.e. from 15°-25° to 0°.
  • the cylinder 41 of the hydropneumatic piston has a longitudinal groove 44 formed on the inner surface of the same cylinder.
  • Such groove 44 extends longitudinally with width and/or depth varying as a function of the longitudinal position for at least a part of the cylinder 41, as shown schematically in Figure 10 . Due to this groove 44, it is possible to easily differentiate the internal sections of the cylinder 41 in the various longitudinal portions 41a, 41b, 41c without changing the overall shape of the cylinder.
  • the hydropneumatic piston 40 may also act as a damper due to the viscous damping effect provided. This guarantees an impact-resistant effect. If the door is thrown closed with a higher speed than would have occurred if left free to close by itself, it slows down automatically due to the aforementioned viscous damping. The piston 40 then absorbs the extra energy given by the thrust and disperses it in the form of heat.
  • a refrigerated cabinet has been constructed with a door equipped with an automatic closing system according to the invention, using a hydropneumatic piston having a ratio equal to 1.21 between the force F (of extension) generated in the initial compression phase and the force F (of extension) generated in the final compression phase.
  • the following are shown in the graphs of Figure 10 - depending on the angle of opening of the door and the stroke of the piston stem - the trend of the stress on the door handle in opening (graph B) and in closing (graph C) and the trend of the closing speed (graph V).
  • the trend of the stresses (opening and closing) on the handle reflects the trend of the angular momentum in opening and closing.
  • the closing stress decreases as the angle of opening of the door increases, until it substantially nullify itself at an angle of opening between 80° and 85°.
  • Such angular values therefore correspond to zero angular momentum or one so low that the friction of the hinges is not overcome.
  • angular momentum varies substantially only as a function of the arm B, which decreases as the angle of opening increases.
  • force F generated by the piston may be considered substantially constant.
  • the closing speed decreases as the closing angle is reduced: it remains at a substantially constant high value from 85° to about 50°, and then progressively decreases to a minimum value at 0°.
  • the present invention offers several advantages, some of which have already been described.
  • the automatic door closing system in the refrigerated cabinet according to the invention allows simultaneously for violent impacts between door and frame to be avoided and for the closing time of the same door to be minimized.
  • the automatic door closing system in the refrigerated cabinet according to the invention allows the door to stop in a defined open position without the use of additional door stop devices with respect to the automatic closing system of the door.
  • the automatic closing system of the door in the refrigerated cabinet according to the invention is simple and inexpensive to produce as it does not require the installation of complex devices. In particular, it may be achieved with devices (see hydropneumatic pistons) available on the market and less expensive than hydraulic systems.

Claims (13)

  1. Kühlmöbel mit einer oder mehreren automatisch schließenden Türen, umfassend einen Stütz- bzw. Trägerrahmen (2), der ein Ladefach (3) definiert, und zumindest eine Tür (10), die das Ladefach (3) verschließt, wobei die Tür (10) mit dem Rahmen (2) durch Scharniermittel (20; 30) verbunden ist, die eine vertikale Drehachse (X) definieren, um die sich die Tür (10) drehen kann, um sich zwischen einer geschlossenen Position und einer vordefinierten Position maximaler Öffnung zu bewegen, wobei das Möbel (1) ein automatisches Schließsystem der zumindest einen Tür (10) umfasst, wobei das automatische Schließsystem einen hydropneumatischen Kolben (40) umfasst, der - an seinen beiden gegenüberliegenden bzw. entgegengesetzten Enden (40a, 40b) entlang einer dynamischen Aktionsachse (Y) davon - jeweils an den Rahmen (2) und an die Tür (10) angelenkt ist, wobei der hydropneumatische Kolben (40) an der Tür in einer versetzten Position in Bezug auf die Drehachse (X) der Tür (10) mittels einer Hebelverlängerung (43) angelenkt ist, die drehfest mit der Tür (10) ist und sich von der Tür (10) zu dem Inneren des Möbels (1) erstreckt, wobei die beiden Anlenkpunkte des hydropneumatischen Kolbens (40) an dem Rahmen (2) und an der Hebelverlängerung (43) in Bezug auf die Drehachse (X) so positioniert sind, dass:
    - zwischen der geschlossenen Position und der Position maximaler Öffnung der hydropneumatische Kolben (40) eine Kraft (F) auf die Hebelverlängerung (43) entlang seiner dynamischen Aktionsachse (Y) ausübt, die immer um die Drehachse (X) ein Winkelschließmoment (M) der Tür (10) entwickelt; und
    - die senkrechte Distanz (B) zwischen der dynamischen Aktionsachse (Y) des hydropneumatischen Kolbens (40) und der Drehachse (X), die den Arm des Winkelmoments (M) definiert, in dem Maße abnimmt, wie der Winkelöffnungsgrad der Tür (10) um die Drehachse (X) herum zunimmt, und zwar im Wesentlichen bis er bzw. sie sich in der vorbestimmten Position maximaler Öffnung aufhebt, so dass in der vorbestimmten Position maximaler Öffnung das Winkelmoment (M) Null ist und die Tür (10) automatisch im Gleichgewicht bleiben kann,
    wobei der Zylinder (41) des hydropneumatischen Kolbens (40) zumindest zwei Längsabschnitte mit unterschiedlichen Innenquerschnitten aufweist, wobei ein erster Abschnitt (41a) einen größeren Innenquerschnitt aufweist als der zweite Abschnitt (41b), so dass der Kopf des Schafts (42) des Kolbens (40) an dem ersten Abschnitt (41a) weniger Gleitwiderstand erfährt als an dem zweiten Abschnitt (41b) und schneller gleiten kann, wobei der hydropneumatische Kloben (40) in Bezug auf die Drehachse (X) derart ausgerichtet ist, dass sich der Kopf des Schafts (42) in den ersten Abschnitt (41a) hinein bewegt, wenn sich die Tür (10) in dem Öffnungswinkelbereich zwischen der Position maximaler Öffnung und einer ersten vordefinierten Zwischenwinkelposition bewegt, und derart, dass sich der Kopf des Schafts (42) in den zweiten Abschnitt (41b) hinein bewegt, wenn sich die Tür (10) in dem Öffnungswinkelbereich zwischen einer zweiten vordefinierten Zwischenwinkelposition und der geschlossenen Position bewegt.
  2. Kühlmöbel nach Anspruch 1, wobei die beiden Anlenkpunkte des hydropneumatischen Kolbens (40) an dem Rahmen (2) und an der Hebelverlängerung (43) in Bezug auf die Drehachse (X) derart positioniert sind, dass der hydropneumatische Kolben (40) selbst in der geschlossenen Position eine Kraft (F) ausübt, über welche die Hebelverlängerung (43) um die Drehachse (X) herum ein Winkelmoment (M) entwickelt, das die Tür (10) statisch geschlossen hält.
  3. Kühlmöbel nach Anspruch 1 oder 2, wobei der Kolben (40) an einem oberen Abschnitt des Möbels (1) an dem Rahmen (2) angelenkt ist, während der Kolben (40) an der Tür (10) mittels der Hebelverlängerung (43) an einem oberen Abschnitt der Tür angelenkt ist, wobei sich vorzugsweise die beiden Anlenkpunkte des Kolbens (40) an dem Rahmen (2) und an der Tür (10) im Wesentlichen auf der gleichen vertikalen Höhe befinden.
  4. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, wobei sich der Anlenkpunkt (40a) des Kolbens (40) an dem Rahmen (2) in einer zurückgezogenen Position in Richtung der Innenseite des Möbels in Bezug auf eine vertikale Ebene (V) befindet, die durch die Tür (10) in der geschlossenen Position definiert ist, wobei die Drehachse (X) auf der vertikalen Ebene (V) liegt.
  5. Kühlmöbel nach Anspruch 4, wobei die Hebelverlängerung (43) so bemessen ist, dass der Anlenkpunkt (40b) des Kolbens (40) an der Tür (2) sich immer in der zurückgezogenen Position in Richtung der Innenseite des Möbels in Bezug auf die vertikale Ebene (V) befindet, die durch die Tür (10) in der geschlossenen Position definiert ist.
  6. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, wobei der hydropneumatische Kolben (40) hinter der Tür (10) positioniert ist und wobei die beiden Anlenkpunkte des hydropneumatischen Kolbens (40) an dem Rahmen (2) und an der Hebelverlängerungen (43) in Bezug auf die Drehachse (X) derart positioniert sind, dass der hydropneumatische Kolben (40) bei der Öffnungsbewegung der Tür zwischen der geschlossenen Position und der Position maximaler Öffnung immer zusammengedrückt wird und immer eine Kraft (F) ausübt, die von dem Anlenkpunkt an dem Rahmen (2) in Richtung des Anlenkpunkts an der Hebelverlängerung (43) entlang seiner dynamischen Aktionsachse (Y) gerichtet ist, wobei sich die Hebelverlängerung (43) vorzugsweise von der Tür (10) in Richtung der Innenseite des Möbels (1) erstreckt.
  7. Kühlmöbel nach Anspruch 6, wobei der hydropneumatische Kolben (40) an dem Rahmen (2) an dem Zylinder (41) angelenkt ist und an der Tür (10) an dem Schaft (42) angelenkt ist.
  8. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, wobei der hydropneumatische Kolben (40) eine im Wesentlichen konstante Kompressionskraft (F) als Funktion des Kompressionsgrades des Kolbens erzeugt, wobei vorzugsweise das Verhältnis zwischen der Kraft (F), die in der initialen Kompressionsphase erzeugt wird, und der Kraft (F), die in der finalen Kompressionsphase erzeugt wird, zwischen 1,2 und 1,4 liegt.
  9. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Zylinder (41) des hydropneumatischen Kolbens (40) einen Zwischenlängsabschnitt (41c) umfasst, der zwischen dem ersten (41a) und dem zweiten (41b) Längsabschnitt (41c) vorhanden ist und einen inneren Verbindungsquerschnitt zwischen dem Querschnitt des ersten (41a) und des zweiten (41b) Abschnitts aufweist, so dass an dem Zwischenabschnitt (41c) der Kopf des Schafts (42) des Kolbens (40) einen Gleitwiderstand im Vergleich zu dem erfährt, auf den er in dem ersten (41a) und dem zweiten (41B) Abschnitt trifft, und darin mit einer Zwischengeschwindigkeit gleitet, bei der der Kopf des Schafts (42) in den Zwischenabschnitt (41c) übergeht, wenn sich die Tür (10) in der Winkelöffnung zwischen der ersten und der zweiten vordefinierten Zwischenwinkelposition bewegt.
  10. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, wobei der Zylinder (41) zumindest eine Längsnut (44) aufweist, die an seiner Innenfläche bzw. -oberfläche ausgebildet ist, wobei sich die Nut (44) longitudinal mit einer Breite und/oder Tiefe erstreckt, die in Abhängigkeit von der Längsposition für zumindest einen Teil des Zylinders (41) variiert bzw. variieren, wobei die Nut (44) die Abmessungen des Innenquerschnitts der Längsabschnitte (41a, 41b, 41c) des Zylinders (41) in Längsrichtung differenziert.
  11. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, wobei die Scharniermittel ein oberes Scharnier (20), das an der Oberseite des Rahmens (2) des Möbels befestigt ist, und ein unteres Scharnier (30) umfassen, das an der Basis des Rahmens (2) des Möbels (1) befestigt ist, wobei das obere Scharnier (20) und das untere Scharnier (30) miteinander ausgerichtet sind und die Drehachse (X) definieren.
  12. Kühlmöbel nach einem oder mehreren der vorhergehenden Ansprüche, umfassend mechanische Anschlagmittel (50), die geeignet sind, einen Begrenzungsanschlag für die Tür zu definieren, der einen Öffnungswinkelwert aufweist, der nicht kleiner als derjenige ist, der der Position maximaler Öffnung entspricht, wobei die mechanischen Anschlagmittel (50) geeignet sind zu verhindern, dass die Tür (10) beim Öffnen gezwungen wird, wodurch der hydropneumatische Kolben (40) belastet wird.
  13. Kühlmöbel nach den Ansprüchen 11 und 12, wobei die mechanischen Anschlagmittel (50) an dem unteren Scharnier (30) positioniert sind.
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CN212428411U (zh) * 2020-07-29 2021-01-29 承德特耐力门控科技有限公司 一种气动自动回位装置
WO2023100041A1 (en) * 2021-12-03 2023-06-08 Cisaplast S.P.A. Door-closing device for refrigeration cabinets
CN114809845A (zh) * 2022-05-10 2022-07-29 浙江亚厦装饰股份有限公司 一种自润滑静音闭门器及其安装方法

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EP1619409B1 (de) 2004-07-22 2008-01-23 Stabilus GmbH Gasfeder mit Endlagendämpfung
US20080189906A1 (en) 2005-04-26 2008-08-14 Suspa Holding Gmbh Hinge Arrangement

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