NL2027726B1

NL2027726B1 - Sliding door rail system for closing an opening in a wall

Info

Publication number: NL2027726B1
Application number: NL2027726A
Authority: NL
Inventors: Christian Ostermeier Jacob
Original assignee: Metaflex Doors Europe B V
Priority date: 2021-03-09
Filing date: 2021-03-09
Publication date: 2022-09-26

Abstract

Sliding door rail system for closing an opening in a wall, wherein the system includes a guide rail (1) and a sliding assembly (2) that is displaceable along the guide rail (1), wherein the guide rail is provided with an closing section (1a), wherein the sliding assembly (2) and closing section (1a) of the rail are conﬁgured such that a door panel (9) of the sliding assembly (2) is displaceable towards the opening in a direction (Rt) substantially perpendicular to a plane (P) of the opening and wherein at the same time the door panel (9) is displaceable in a direction (Rd) downwardly, wherein the sliding door rail system includes a pressure assembly (10) conﬁgured to generate a force to assist moving the sliding assembly (2) from a closed position back towards an open position, wherein the pressure assembly (10) is at least partly vertically movable with respect to the guide rail (1).

Description

P129441NL00 Title: Sliding door rail system for closing an opening in a wall The invention relates to a sliding door rail system for closing an opening in a wall, wherein the system includes a guide rail and a sliding assembly that is displaceable along the guide rail.

Such systems, which can be used to hermetically close conditioned spaces, for example room-sized freezers, or operating rooms in hospitals, are generally known, for example from the Dutch patent NL2011353 by the same applicant,. Therein, a sliding assembly, to which a door panel is attached, comprises a wedge-shaped member that is configured to cooperate with another wedge-shaped member, attached to a guide rail. During contact between both wedge-shaped members, the door panel can be moved towards an opening in a wall to close it, wherein the door panel moves downwardly during the closing. Upon release of one wedge-shaped member from the other, the door panel can be moved away from the opening. In the known system, the sliding assembly includes a closing mechanism having a pre-tension device that is connected with a first end thereof to a frame of a first part of the closing mechanism and with a second, opposing, end to a frame of a second part of the closing mechanism. The pre-tension device comprises at least one of a compression spring, a tension spring, a gas spring, a hydraulic spring, at least two magnets arranged with opposing similar poles.

The present invention aims to provide an improved sliding door rail system. In particular, the invention aims to provide a system that can provide light operator-friendly handling, wherein the system can be made sturdy and durable, provides reliable operation, and can be manufactured in an economical manner.

According to an aspect of the invention there is provided a system that is characterized by the features of claim 1.

According to an embodiment there is provided a sliding door rail system for closing an opening in a wall, wherein the system includes a guide rail and a sliding assembly that is displaceable along the guide rail, wherein the guide rail is provided with an closing section, wherein the sliding assembly and closing section of the rail are configured such that a door panel of the sliding assembly is displaceable towards the opening in a direction substantially perpendicular to a plane of the opening and wherein at the same time the door panel is displaceable in a direction downwardly, wherein the sliding door rail system includes a pressure assembly configured to generate a force to assist moving the sliding assembly from a closed position back towards an initial position, wherein the pressure assembly is at least partly vertically movable (and preferably also at least partly horizontally) with respect to the guide rail.

In this way, the system can provide light operator-friendly handling, since the pressure assembly can assist the operator in lifting or displacing the door during its opening movement.

Still, the system can be provided in a sturdy, relatively compact and durable configuration, and can provide reliable operation.

Also, the system can be made with relatively little components, for example such that the sliding assembly itself does not require spring means for assisting door lifting operation, so that it can be manufactured in an economical manner.

According to an embodiment the system can be used with a heavy door panel (e.g. a door having a mass of at least 200 kg, preferably at least 300 kg), alternatively, the door panel can be relatively light-weight as such or have a mass smaller than 200 kg (e.g. a mass in the range of 25-100 kg). Further, an aspect of the invention provides a pressure assembly, in particular a pressure assembly that is evidently destined to be part of a system according to the invention.

The innovative the pressure assembly can be configured to generate a force to assist moving a sliding assembly from a closed position back towards an initial position after mounting,

wherein the pressure assembly is at least partly vertically movable (and preferably also at least partly horizontally) with respect to a mounting position, for example a position of a respective mounting structure. In this way, above-mentioned advantages can be achieved.

The present invention will be further elucidated with reference to figures of exemplary embodiments. Therein, corresponding elements are designated with corresponding reference signs.

Figure 1 shows a perspective view of a sliding door panel attached to a sliding door rail assembly, when the door is in an opened position; Figure 2 is similar to Fig. 1, showing a respective closed door position; Figure 3 is similar to Fig 1, showing a non-limiting example of a system according to the invention, at a first position of a sliding assembly; Figure 4 is similar to Fig 3, showing the sliding assembly in a second position; Figure 5 is similar to Fig. 3, showing a third position of the sliding assembly; Figure 6 is similar to Fig. 3, showing a closed position of the sliding assembly; Figure 7A shows a side view of part of a rail of an example of the system shown in Figures 3-6; Figure 7B is a cross-section over line VII-VII of Fig. 7A. Figure 8 depicts a perspective side view of an example of a pressure assembly of a system shown in Figures 3-6; Figure 9 depicts a partly opened up perspective bottom view of the pressure assembly of Fig. 8, with a mounting frame; Figure 10 depicts another opened-up perspective bottom view of the pressure assembly of Fig. 8, with a mounting frame; Figure 11 depicts a perspective top view of the pressure assembly of Fig. 8, without mounting frame; and

Figure 12 is similar to Fig. 11, showing the additional mounting frame.

Figures 1 and 2 show a perspective view of a system that includes sliding door panel 9 attached to a sliding door rail assembly 2. The sliding door rail assembly comprises a guide rail 1 and at least one, and in this case two, sliding assemblies 2 movable along the guide rail 1. The guide rail 1 can comprise at least one substantially horizontal support surface 3 (see also Figures 7A, 7B, showing an example of the guide rail 1 in more detail), for supporting the one or more sliding assemblies 2. The support surface 3 can e.g. substantially extend along a surface H. The door panel 9 is configured to close an opening 22 in a wall, for example hermetically, for example an access to a conditioned space, for example a room-sized freezer, or an operating room in a hospital. The door can be brought from an opened position (Figure 1) to a closed position (Figure 2), by moving the door in a first direction X (i.e. a closing direction). The door can be moved in an opposite direction X’, i.e. back, to said opened position manually, or via an automated driving system, well-known by a person skilled in the art.

According to an embodiment, for example, one or more resilient sealing members 50, for example rubber strips or strips made or rubber-like material, may be provided along the door opening 22, the sealing members e.g. be provided on a respective door frame or wall structure that defines the door opening. During a door closing movement, the door 9 can be pressed onto such sealing members 50 (leading to elastic deformation thereof) to provide improved sealing of the door opening 22.

Figures 3 shows a further embodiment, of a sliding door rail system for closing an opening 22 in a wall, the system including a guide rail 1 and a sliding assembly 2 that is displaceable along the guide rail 1. The system can be configured for mounting of (i.e. holding, suspending) a relatively heavy door 9 having a mass of at least 200 kg, for example at least 250 kg or at least 300 kg. Alternatively, a door having a lower mass can be installed.

As follows from the drawings, the guide rail 1 can be provided with a closing section la, wherein the sliding assembly 2 and corresponding closing section 1a of the rail can be configured such that a door panel 9 of the sliding assembly 2 1s displaceable towards the opening in a substantially 5 horizontal (transversal) direction R; substantially perpendicular to a plane P of the opening and wherein at the same time the door panel 9 is displaceable in a direction Ra downwardly (see Figures 7A, 7B indicating the respective directions with respect to the rail 2). In case several spaced-apart sliding assemblies 2 are present, the rail can include several corresponding spaced-apart closing sections la, as will be clear to the skilled person.

For example (see Fig. 7), the guide rail 1 (i.e. its respective rail profile) can include an elongated (flat, strip-shaped) rail section 1s (e.g. a first rail flange), an upper surface of which provides the support surface 3. Viewed in a vertical cross-section, normally with respect to a center line of the rail (see Figure 7B), the an elongated strip-shaped rail section 1s can include an angle B with a vertical plane V (i.e. a plane V extending in parallel with respect to a center line of the rail), for example an angle Bin the range of about 25 -65 degrees, in particular an angle in the range of about 40-50 degrees, for example an angle of about 45 degrees. The guide rail 1 can include further elongated rail sections It, lu, lv (i.e. rail flanges), for example a lower flange 1t, extending e.g. horizontally, and e.g. reaching inwardly from a lower part of the first section 1s, a back flange 1u, extending e.g. vertically, the back flange 1u being spaced apart from the support section 1s by the lower flange 1t, and an optional top flange 1v, extending for example horizontally, the top flange 1v extending from an upper side/edge of the back flange 1u. One or more of these further rail flanges can include mounting sections or apertures, for mounting the rail to a support structure (e.g. a wall, support beam or the like), using suitable fasterners as will be appreciated by the skilled person.

Each sliding assembly 2 can be a wheeled structure 2, 28, 29 that is connectable to a door panel 9, the wheeled structure being slidably supported on the guide rail 1, in particular on a respective support surface

3. For example, each sliding assembly 2 can include a number of wheels 28 (for example only one or two or three) that are movably supported on respective sections of the support surface 3 of the guide rail 1. The one or more wheels 28 of each sliding assembly 2 can be directly (rotatingly) coupled to the door, but it is preferred that the wheel or wheels 28 is/are connected via a connecting structure 29, for example a frame or connecting profile, in which case each wheel can be rotatingly held by the connecting structure 29, whereas that structure 29 can be fixed to the door using suitable fasteners, e.g. bolting means. In an embodiment, an axis 28a of rotation of each wheel 28 of each sliding assembly 2 is a horizontal axis (as in the drawings).

According to an embodiment, each closing section la of the rail can be provided by part of an elongated (flat, strip-shaped) rail section 1s that includes an afore-mentioned angle B with the afore-mentioned vertical plane V.

For example, each closing section 1a of the guide rail 1 can include at least one sloping section la for providing the downward displacement of a respective sliding assembly 2 (when that assembly, e.g. a respective wheel 28, is moved along the closing section 1a in the closing direction X). Each sloping section can e.g. be provided by a suitable slope of the support surface of the guide rail 1, see e.g. Figures 3-7A. In particular, a supporting section of the rail 1, for example a said elongated rail section 1s (first flange) can include a local indent K that provides the sloping section la. In case a sliding assembly includes more than one wheel, for example two spaced- apart wheels 28, the closing section 1a of the guide rail 1 can include more than one (e.g. two) corresponding sloping sections 1a for receiving and downwardly guiding the wheels 28 (and additionally moving the wheels towards the door opening, in the substantially horizontal direction R‚) when the sliding assembly moves in the closing direction X.

In that case, the wheels 28 and respective sloping sections la can be arranged such that the wheels 28 are simultaneously received by the sloping sections la during respective movement along the rail 1. According to an embodiment, each sloping section of the rail can include a constant angle with a horizontal plane H (i.e. a plane that includes a horizontal part of the rail support surface 3), for example an angle in the range of about 1-15 degrees, in particular an angle in the range of about 8- 12 degrees.

According to a preferred embodiment, the sloping section 1a encloses a non-constant angle with the horizontal plane H (viewed along a horizontal movement direction X of the sliding assembly). In this way, improved door closing can be achieved, for example such that the door can be held stably in a closed position, and/or can be pressed tightly to a closed door position, for example onto sealing afore-mentioned members 50 Gf present). The closing section of the rail can include for example two sloping sections lai, la: (see Fig. 7A) that extend at mutually different angles gl, 2 with respect to the horizontal plane H.

A first sloping section la; can for example include a first sloped, straight section of the support surface that includes a first angle @1 with the horizontal plane, and a second sloping section lag can for example include a section sloped, straight section of the support surface that includes a second (different) angle @2 with the horizontal plane H.

The first sloping section la; can be an initial part of the closing section la that is encountered first by the sliding assembly 2 during a respective closing movement, and a respective section sloping section 142 can be a subsequent part of the closing section 1a that is encountered subsequently by the sliding assembly 2 during the respective closing movement.

In particular, the second angle @2 can be larger than the first angle gl, in particular for providing increase of a (gravity induced) closing force of the door so that improved closure of the door opening 22 can be achieved.

As an example, the first angle pl can be smaller than 12 degrees, for example an angle in the range of about 1-10 degrees.

The lager second angle @2 can be at least 12 degrees (or for example in the range of 10-20 degrees), and such that the second angle ¢2 is larger than the first angle gl.

Further, each of adjoining sloping sections lai, laz of a rail closing section may be linearly sloping (at constant angles) but that is not required.

According to an embodiment, one or each sloping section of the rail can include a curved sloping section, as will be appreciated by the skilled person.

Alternatively or additionally, a curved sloping section may have a relatively large angle of curvature such that the section includes a slightly deviating angle with the horizontal plane H viewed along a longitudinal rail direction.

Also, the closing section la of the guide rail 1 can include one or more one sloping sections each including a substantially constant angle with a horizontal plane H as well as one or more curved sloping sections (e.g. extending between the constant angle sloping sections). A maximum depth Ul of a said sloping section (i.e. a vertical distance between a bottom of the respective slope and the initial horizontal part of the rail support surface 3) can be relatively small, for example a depth of at most 1-2 cm and preferably a depth U1 smaller than 1 cm, such as a depth Ul in the range of about 3-9 mm.

Thus, preferably, during its closing movement, the respective sliding assembly 2 (and a door held thereby after assembly) can translate over a vertical distance (in the direction Ra) of at most 1-2 cm and preferably less than 1 cm, for example a horizontal distance in the range of about 3-9 mm.

Also, for example, during its closing movement, the respective sliding assembly 2 (and a door held thereby after assembly) can translate over a horizontal distance (in the direction R;) of at most 1-2 cm and preferably less than 1 cm, for example a horizontal distance in the range of 6-9 mm.

A length U2 of the sloping section 1a of the rail 1, measured in parallel with a rail center line, can e.g. be smaller than about 15 cm, e.g. (but not limited to) the range of at most about 10-12 cm.

A closing movement, in said closing direction X, of an embodiment is depicted in Figures 3-6. Figure 3 shows in initial opened position of a gliding assembly 2 wherein it is spaced apart from a closing section 1a of the respective rail 1. When the gliding assembly 2 is moved in its closing direction X, it encounters the closing section la first (see Figure 4), and subsequently moves downwardly (in the direction Rg) as well as horizontally (in the substantially horizontal direction R:) as in Figure 5, towards a final closed position that is shown in Figure 6. In that closed position, respective wheels of the gliding assembly 2 have rolled onto the bottoms of respective downward slopes of the corresponding closing sections 1a of the rail 1. An opening movement involves moving the gliding assembly 2 in an opposite direction X’ along the rail 1 (i.e. opposite to the closing direction X), such that gliding assembly 2 is lifted via the sloped parts of the rail support surface to a respective horizontal main support section of the rail.

Advantageously, according to an embodiment, the sliding door rail system can include a pressure assembly 10 configured to generate a force to assist moving the sliding assembly 2 from a closed position back towards an initial position (i.e. in a direction X opposite to the closing direction X), in which initial position the sliding assembly 2 can be back on a horizontal part of the rail 1 (i.e. the sliding assembly 2 is removed from/out of the closing section la of the rail). According to a preferred embodiment, the pressure assembly 10 is at least partly vertically movable with respect to the guide rail 1 (and/or at least partly vertically movable with respect to a position of a respective mounting structure 14, see the drawings). Preferably, the pressure assembly 10 is also at least partly horizontally movable with respect to the guide rail 1 (and/or at least partly horizontally movable with respect to a position of a respective mounting structure 14, see the drawings).

Figures 3-6 show an example of a pressure assembly 10 that is associated with the rail 1. Further details concerning an exemplary pressure assembly 10 are depicted in Figures 8-12.

The pressure assembly 10 can include a pressing member 11, arranged to move substantially in parallel with respect to the guide rail 1 after mounting, in particular in a substantially horizontal direction.

According to an embodiment, the pressing member 11 can reach outwardly from a housing of the pressure assembly 10 (for receiving the sliding assembly 2), to be pressed inwardly (into and/or through its housing) by a closing sliding assembly. For example, the pressing member 11 can have a distal end 11a for receiving and contacting the sliding assembly 2 during respective movement assistance (i.e. to push against the sliding assembly 2 with a pressure assembly generated force). According to an embodiment, a proximal end of the pressing member 11 is (also) located outside a respective housing of the pressure assembly. According to an embodiment, a surface area of the respective contact surface (i.e. distal end 11a) end of the pressing member 11 can be relatively small, e.g. smaller than 25 cm? e.g. smaller than 10 cm? and in particular smaller than 4 cm?2, more in particular smaller than 2 cm?.

In particularly, the pressing member 11 can be movable between a first, idle state (shown in Figure 3) and a second, retracted state (see Figure 6). As will be explained below, preferably, spring means 12, 13 are provided to counteract a movement of the pressing member 11 from its first to its second position, and to provide the pressure assembly force. A respective force, generated by the pressure assembly 10, can e.g. be a substantially horizontal force (i.e. a force that is substantially in parallel with respect to a longitudinal rail direction).

Further, the pressing member 11 can be at least partly vertically movable with respect to the guide rail 1, after mounting. The sliding assembly 2 can e.g. be receivable by the pressure assembly 10 to be pressured thereby, the first the sliding assembly 2 in particular including a force receiving section 2F facing the pressure assembly 10. As an example, the force receiving section 2F can be an integral part of a connecting structure 29 of a wheeled sliding assembly 2.

The pressing member 11 of the pressure assembly 10 can be configured in various ways; according to an embodiment the pressing member includes or consists of an elongated rod or element 11, that is linearly translatable along a respective center line, between a respective first and second pressing member position. For example, the pressing member 11 can have one translational degree of freedom (i.e. along a longitudinal direction of the pressing member 11).

The pressure assembly 10 can include a mounting structure 14, for example a housing, for connecting the pressure assembly to an external support structure, for example to the rail 1. According to a preferred embodiment the mounting structure 14 has a first section 14a for shidingly holding the pressing member 11, in particularly such that the pressing member 11 is linearly translatable along a respective center line. Further, it is preferred that the mounting structure has a second section 14b (e.g. a coupling frame) for movably holding the first section 14a. According to an embodiment, the first section 14a of the mounting structure 14 can be pivotally or swivably coupled to the second section 14b of the mounting structure 14, for example over an angle of at least 1 degrees, for example an angle in the range of about 1-25 degrees. In particular, the mounting structure 14 can allow a pivotal movement of the pressing member 11 from an initial, substantial horizontal orientation (as is shown in Figures 3, 4) towards a downwardly pivoted orientation (shown in Figure 6), in particular such that a distal end 11a of the pressing member can move downwardly (in downward direction Rg) along with the sliding assembly 2 during mutual contact (i.e. when the sliding assembly moves towards its closing position).

According to a further preferred embodiment, the pivotal connection can also be such that that a distal end 11a of the pressing member can move in the transversal direction Rt (i.e. in a horizontal direction) along with the sliding assembly 2 during mutual contact (i.e. when the sliding assembly moves towards its closing position).

It follows that a respective pivot axis of the first section 14a of the mounting structure 14, with respect to a stationary second section 14b, can be a horizontal axis, a vertical axis or both (allowing pivoting/turning in both directions) For example, the first section 14a can be pivotally suspended from the second section 14b, using respective suspension means, for example a number of connectors 35 that pivotally or swivably couple the sections 14a, 14b to each other. For example, it follows that the first section 14a preferably has two rotational degrees of freedom with respect to the second section 14b (via respective suspension means), for example a first rotational degree of freedom over a horizontal axis of rotation (the horizontal axis of rotation in particular extending normally with respect to the plane P of the door opening 22) and a second rotational degree of freedom over a vertical axis of rotation. Similarly, the respective pressing member 11 can have two rotational degrees of freedom (in addition to a respective translational degree of freedom), i.e. a first rotational degree of freedom over said horizontal axis of rotation and a second rotational degree of freedom over said vertical axis of rotation.

Optionally, the pressure assembly 10 can include spring means 15 configured for maintaining the first section 14a in an initial (idle) horizontal position. Such spring means can be configured in various ways, and can include e.g. resilient material located between the first section 14a and second section 14b, or for example one or more spring members. An example includes two parallel coil springs 15, extending next to each other and being connected with respective first ends to a distal part of the swivable section 14a of the mounting structure and connected with proximal ends to spring attachment means 16 of the fixed/stationary second section 14b of the mounting structure 14. In particular, the coil springs 15 extend in parallel with respect to the pressing member 11. It is preferred that the spring means 15 are pretensioned, for maintaining the movable section 14a of the mounting structure in an initial, idle, state (see Fig. 3). It will be appreciated that such spring means can be configured in various ways, and can include or be provided by one or more leaf springs, coil springs, resilient (rubber or rubber-like) material and/or the like.

Further, advantageously, the pressure assembly 10 can include one or more spring means 12, 13 configured to counteract movement of the pressing member 11 from its first, initial (idle) position to its second (retracted) position. In particular, the spring means 12, 13 can be tensioned (to a certain maximum spring force), e.g. by or via an inwardly moving pressing member 11, when the sliding assembly is moved to a closed position (and moves the pressing member 11 towards its second, retracted position). A respective maximum spring force, provided by the spring means 12, 13 can be relatively large, for example a spring force that is at least 150 Newton, preferably at least 500 N, for example at least 800 N, in particular at least 1200 N, so that the system is capable to be used for conveniently and reliably operating relatively heavy doors. In particular, said maximum spring force is the force that is generated by the pressing assembly 10 (e.g. respective spring means 12, 13) when the sliding assembly 2 is in its closed position (see Fig. 6), i.e. when the pressing member 11 is in its second position (and a respective door panel is in a closed position). The spring force of the spring means 12, 13 can provide the force to assist moving the sliding assembly 2 from a closed position back to its open position. Said maximum spring force can also be lower than 150 Newton, for example in case a door panel 9 of a smaller mass is mounted.

The maximum spring force of the spring means 12, 13 is preferably such that the sliding assembly 2 and a respective door panel 9 remain in their closed positions.

In other words, the maximum spring force generated by the spring means 12, 13 when the respective pressing member 11 15 in its second position is smaller (by a certain amount) than a threshold force (e.g. a horizontal force applied manually by an operator to the door panel 9) required for horizontally moving the sliding assembly 2 (mounted to the door panel 9) out of the sloped section 2a of the rail, in the opening direction X’. It 1s preferred that said maximum spring force is adjustable, e.g. by respective spring adjustment means.

Also, it is preferred that a difference between said maximum spring force and said threshold force (required for initiating movement of the sliding assembly back in the opening direction X) is in the range of 1-20 Newton, for example a range or 1-10 Newton.

Advantageously, the spring means 12, 13 are provided by coil springs, in particular coil springs mounted concentrically with respect to the pressing member 11 (see Fig. 10), so that a durable and reliable configuration can be provided.

Also, each of the spring means 12, 13 preferably provides a spring force that linearly varies with respect to axial spring length, which is particularly advantageous in case of corresponding rail sloping sections lai, lay sloping at respective angles and/or curves.

According to an embodiment, in case the closing section la of the guide rail 1 includes at least one sloping section for providing the downward displacement of the sliding assembly, the pressure assembly 10 is preferably configured to generate a force that is substantially proportional (preferably linearly proportional) to a location of the sliding assembly 2 with respect to the sloping section.

Further, in case the sloping section encloses a non- constant angle with a horizontal plane viewed along a horizontal movement direction of the sliding assembly (the closing section for example including at least two sloping sections that extend at mutually different angles with respect to the horizontal plane), it is preferred that the pressure assembly

10 is configured to generate a non-linearly decreasing force during moving the sliding assembly 2 from the closed position back towards its initial position (i.e. out of the sloping rail section), in particularly such that the decease of the force is associated with the angle of the slope.

Referring to Figures 7A and 10, in case the closing section of the rail includes for example two sloping sections lai, lag that extend at mutually different angles @1, q2 with respect to the horizontal plane H, the spring means 12, 13 of the pressure assembly 10 preferably includes a first coil spring 12 that at least corresponds with the first sloping section lai,of the rail, to counteract movement of the sliding assembly 2 along that first sloping section. The spring means of the pressure assembly 10 preferably includes a second coil spring 13 that corresponds with the second sloping section 14: of the rail, to counteract movement of the sliding assembly 2 along that second sloping section. In a further embodiment, the first coil spring 12 can be arranged to correspond with the second sloping section 142 of the rail as well, thereby providing joined action with the second coil spring 13 when the sliding assembly 2 moves along the second sloping section laz of the rail, which is in particular advantageous in case the sloping angle p2 of the second sloping section 142 is larger than the sloping angle gl of the first sloping section la.

For example, the spring means 12, 13 can include concentric coils springs, optionally wound in mutually opposite directions. The first coil spring 12 can be longer than the second coil spring 13, in particularly such that a working length of the first coil spring 12 corresponds to a total length of the sloping section 1a of the rail (i.e. the total length of the sloping sections lai, lag), whereas a working length of the second coil spring 13 corresponds to a length of the second sloping section 142 of the rail. Herein, a spring working length can be defined as an axial spring length between an initial (idle) spring state when the respective pressing member 11 is in its first position and a final (compressed) spring state when the pressing member 11 is in its second position.

It will be appreciated that the pressure assembly 10 can be configured in various ways, to transfer inward movement of the pressing member 11 to respective spring means 12, 13 (that are configured to counteract such movement). For example, the pressing member 11 can include one or more spring coupling members 18, 19 connecting to first ends of respective one or more coil springs 12, 13. Opposite second ends of the one or more coll springs can e.g. be fixed to a housing of the pressure assembly vla respective spring connector 38, 39, e.g. to a said first section 14a of the housing.

The configuration can be such that inward movement of the pressing member 11 (from its first to its second position) leads to movement of the spring coupling members 18, 19 to the respective spring connectors 38, 39, thereby compressing the intermediate coil springs 12, 13. In a further embodiment, the spring coupling member 18 of a first (longer) coil spring 12 can be configured to cooperate with the spring coupling member 19 of the other (shorter) coil spring 13, such that compression of the second coil spring 13 only starts after the first coil spring 1 has been compressed over a first distance (i.e. the first distance corresponding to a first sloping section la; of the rail). For example the spring coupling member 19 of the second coil spring 13 can include a central opening 19A, wherein the pressing member 11 and first coil spring 12 reach through that opening, preferably without contacting the spring coupling member 19 of the second coil spring 13. The spring coupling member 18 of the first coil spring can be received by the spring coupling member 19 of the second coil spring (e.g. via opposite edges or contact surfaces) to provide the afore-mentioned cooperation, i.e. such that the spring coupling member 18 of the first coil spring can press the spring coupling member of the second coil spring towards the opposite spring connectors 38, 39 (in particular when the pressing member 11 is moved along a second part of its inward trajectory,

over a second distance, corresponding with a second sloping section lag of the rail). According to a further embodiment, a spring constant of the second coil spring 13 can be higher than a spring constant of the first coil spring 12. In a preferred embodiment, an axial position of a second coil spring end of each of said coil spring 12, 13 is adjustable, for example via a respective adjustable housing connector 38, 39, for adjusting an initial spring force provided by the respective spring 12, 13. Such adjustment is indicated by double arrows J in Figure 10.

Referring to Figures 3-6, operation of the system can include the following. Therein, the pressure assembly 10 can be mounted to or near an end of the rail 1. For example, a section 14b of a housing of the pressure assembly 10 can be connected to the rail 1, e.g. to a said horizontal or upper rail flange 1v. Further, optional stopping means 40 can be mounted to or near the respective end of the rail 1, behind the pressure assembly, in particular for receiving an opposite end of a respective pressing member 11 to define a respective final (inwardly moved) position. Optionally, such stopping means 40 can be integrated with the pressure assembly or a housing thereof, as will be appreciated by the skilled person.

Initially (see Figure 3), a first sliding assembly 2 of the system can be located at a distance from an opposite, distal end 11a of the pressing member 11 of the pressure assembly. In that case, the pressure assembly 10 1s In an initial, idle state (shown in Figures 8-12). In that case, the spring means 12, 13 of the pressure assembly can be in an initial, relaxed or substantially relaxed state. Optionally, these spring means 12, 13 can be at least partly pretensioned (biased) in their initial spring state.

Also, the said spring means 15 can be in an initial spring state, in particular holding the swivable section 14a of the mounting structure in a first position such that the respective pressing member 11 has a substantially horizontal orientation.

Figure 4 depicts a next step, when the sliding assembly 2 has been moved in a closing direction X towards the pressure assembly 10 and is contacted thereby, in particular at the point wherein the sliding assembly 10 reaches a start of the sloping section 1a of the rail 1. The system is preferably arranged such that first mechanical contact between the distal 11a end of the pressing member 11 and a force receiving section 2F of the sliding assembly 2 occurs when the wheels 28 of the sliding assembly reach upper starting points M (see Fig.

TA) of the respective sloping sections 1a.

Figure 5 depicts a next step, when the sliding assembly 2 has been moved further in the closing direction X, such that it traverses a first part 1a; of the respective sloping section of the rail, and has moved at the respective first angle pl downwardly.

As follows from the above, the corresponding closing movement is such that a respective door panel 9 is displaced towards the door opening 22 in a direction R+ substantially perpendicular to the plane P of the opening and wherein at the same time the door panel 9 is displaced in a direction Ra downwardly.

During this movement, the pressing member 11 is pressed inwardly (i.e. with its distal end moving towards the respective housing 14), wherein the respective spring means 12 start compressing, in particular, the first coil spring 12 due to respective movement of its spring coupling member 18. According to an embodiment, the second coil spring 13 is not compressed yet when the sliding assembly 2 traverses the first part 1a; of the respective sloping section of the rail.

Also, advantageously, during the movement of the pressing member 11, the respective the movable section 14a of the mounting structure (e.g. housing 14) pivots or swivels, particularly such the distal end of the pressing member 11 follows a downward movement of the sliding assembly 2. In particular, the distal end of the retracting pressing member 11 also moves towards the door opening 22 in the direction R+ substantially perpendicular to the plane P of the opening and wherein at the same time in a direction Rq downwardly.

In this way, reliable operation of the system can be achieved, reduction in wear, and improved durability, in particular in case of handling a heavy a door 9. As a result, the horizontally moving pressing member 11 is being tilted to a certain degree, preferably to a slightly tilted orientation with respect to an initial (idle) horizontal orientation.

Figure 6 depicts an optional next step, when the sliding assembly 2 has been moved further in the closing direction X, such that it traverses an optional second part 142 of the respective sloping section of the rail, and has moved at the respective second angle @2 downwardly. As follows from the above, the corresponding closing movement is such that a respective door panel 9 is displaced further towards the door opening 22 in a direction R: substantially perpendicular to the plane P of the opening and wherein at the same time the door panel 9 is displaced further in a direction Ra downwardly, to a final closed door position. During this further movement, the pressing member 11 is pressed inwardly (i.e. with its distal end moving towards the respective housing 14 and its proximal end towards an opposite stop member 40 if available ), wherein the respective spring means 12, 13 compress further, in particular, both the first coil spring 12 and the second coil spring 13 at the same time, due to respective movement of both spring coupling members 18, 19 (wherein the second spring coupling member 19 is pressed inwardly by the first spring coupling member 18). During the further inward movement of the pressing member 11, the respective the first section 14a of the mounting structure (e.g. housing 14) pivots or swivels further, in particular towards a final tilted orientation with respect to an initial (idle) horizontal orientation.

As a result, the door is closed, and the spring means 12, 13 of the pressure assembly member 10 are compressed, and operate on the pressing member 11 with an overall maximum spring force. As is mentioned before, the maximum spring force is preferably lower than a horizontal force required to move the respective sliding assembly (or assemblies) 2 and respective door panel 9 out of respective sloping section(s) of the rail 1, for example lower by at least 1 Newton and preferably lower than at least 10 Newton.

On the other hand, the maximum spring force that is achieved by the spring means 12, 13 (i.e. when they are in their compressed condition) is preferably such that a relatively low minimum horizontal external force (e.g. a manual pulling or pushing force) is required for opening the door panel 9 (i.e. moving each sliding assembly out of a respective sloping section of the rail), and lifting the door 9 away from the door opening, for example a relatively low minimum horizontal external force that is smaller than 350 Newton, e.g. smaller than 100 Newton, for example smaller than 50 Newton, such as in the range of about 25-50 Newton.

Opening of the door panel 9 can be achieved e.g. manually, by pushing or pulling the panel 9 in its opening direction X’, e.g. by applying a said minimum horizontal external force.

As a result, the respective sliding assemblies 2 can slide out of respective sloping sections la of the rail towards a horizontal rail section, wherein the movement is assisted by a relatively high force exerted on the first sliding assembly 2 by the pressure assembly (in particular by the respective, relaxing, spring means 12, 13). Therein, the two coil springs 12, 13 can jointly assist movement when the sliding assemblies 2 move out of the second sections 142 of the sloping rail parts and the first coil spring 12 can assist movement when the sliding assemblies 2 move out of the first sections 1a; of the sloping rail parts.

During the opening movement, the distal end 11a of the retracting pressing member 11 can also move away from the door opening 22 opposite to the direction R; (substantially perpendicular to the plane P of the opening) and at the same time in a upwards direction, together with an opposite (contact) surface of the first sliding assembly 2 (that is contacted by that distal end 11a). As follows from the above, the pressure assembly 10 can achieve a relatively high maximum spring force (in case it isin a maximum spring-loaded state, with compressed spring means 12, 13). Since the pressing member 11 can pivot or swivel back during the door opening assistance provided thereby reliable operation of the system can be achieved, reduction in wear, and improved durability, in particular in case of handling a heavy a door panel 9. Also, as a result, the horizontally moving pressing member 11 can be tilted back from a slightly tilted orientation to an initial (dle) horizontal orientation.

During the tiling movement of the pressing member 11, said spring means 15 are preferably configured to counteract such tilting only to a relatively small (preferably neglectable) degree.

In particular, said spring means 15 can operate such that a respective tiltable section 14a of the housing is held in an intial state (with respect to a stationary section 14b) for holding the pressing member 11 horizontally (against gravity) after the pressing member 11 has lost mechanical contact with the first sliding assembly 2. In the foregoing specification, the invention has been described with reference to specific embodiments of the invention.

It will, however, be evident that various modifications and changes may be made therein without departing from the broader spirit and scope of the invention as set forth in the appended claims.

First of all, the system may be suitable for closing of openings in wall to hermetically close conditioned spaces such as operating rooms, laboratory rooms, clean rooms, and the like rooms.

However, the system may also be used to advantage for closing openings in walls that need not be hermetically closed.

The door panel may have different configurations and dimensions for instance dependent on the kind of room that is has to be closed.

This may also hold for the guide rail of the system.

The different parts of the system may have different shapes, different dimensions and may be made of different materials.

However, other modifications, variations and alternatives are also possible.

The specifications, drawings and examples are, accordingly, to be regarded in an illustrative rather than in a restrictive sense.

In the claims, any reference signs placed between parentheses shall not be construed as limiting the claim. The word ‘comprising’ does not exclude the presence of other features or steps then those listed in a claim. Furthermore, the words ‘a’ and ‘an’ shall not be construed as limited to ‘only one’, but instead are used to mean ‘at least one’, and do not exclude a plurality. The mere fact that certain measures are recited in mutually different claims does not indicate that a combination of these measures cannot be used to advantage.

For example, the system can include additional drive means, for example including a motor, for moving a respective door panel along a respective opening and closing direction. In that case, the pressure assembly 10 can e.g. assist an operator in manually opening the door panel 9 in case of e.g. power failure. In addition, during motorized operation, the pressure assembly 10 provides for installing a relatively low power motor to achieve motorized door panel operation.

Furthermore, the present invention can be applied in combination with a relatively heavy door panel, having a mass of e.g. at least 200 kg, but also with a door panel having a mass lower than e.g. 200 kg, e.g. a mass in the range of 25-200 kg (such as a door having a mass in the range of 25-100 kg). In that case, a respective maximum spring force, provided by the spring means 12, 13 can be relatively small (i.e. smaller than e.g. 150 Newton). For example, the door panel can be a relatively lightweight door panel as such, to be opened and closed using only little (manual) operator force.

In any case, it is preferred that when the door panel and respective sliding assembly are in their closed position, the spring means 12, 13 of the pressure assembly member operate via the pressing member 11 on the sliding assembly with an overall maximum spring force, such that the maximum spring force is only slightly lower than a horizontal force required to move the respective sliding assembly (or assemblies) 2 and respective door panel 9 out of respective sloping section(s) of the rail 1, for example lower by an amount in the range of 1-20 Newton, for example lower by 10 Newton and e.g. lower by about 5 Newton.

As a result, a user only has to apply such a small horizontal force to open the door panel.

Claims

Conclusions

A sliding door track system for closing an opening in a wall, the system comprising a guide rail (1) and a sliding assembly (2) displaceable along the guide rail (1), the guide rail comprising a closing section (1a), wherein the slide assembly (2) and the closing section (1a) of the rail are configured such that a door panel (9) of the slide assembly (2) is displaceable towards the opening (22) in a direction (Ry) substantially perpendicular to a plane (P) of the opening and wherein the door panel (9) is movable in a downward direction (Ro) at the same time, the sliding door track system comprising a pressure assembly (10) configured to generate a force to assist the sliding assembly (2) to move. moving from a closed position back to an open position, wherein the pressure assembly (10) is at least partially movable vertically relative to the guide rail (1).

System according to claim 1, wherein the pressure assembly (10) comprises a pressure member (11) arranged to move parallel to the guide rail (1), in particular in a horizontal direction, the pressure member (11) having a distal end (11a) for receiving and contacting the slide assembly (2) during respective movement assistance, wherein the pressing member (11) is also at least partially movable in vertical direction relative to the guide rail (1).

System according to claim 2, wherein the pressure assembly (10 comprises a mounting structure (14), e.g. a housing, with a first part (14a) for keeping the pressure part (11) slidable and a second part (14b) for keeping it movable of the first part (14a).

A system according to claim 3, wherein the first part (14a) of the mounting structure (14) is pivotally or pivotally coupled to the second part of the mounting structure (14), for instance through an angle of at least 1 degree, for instance an angle in the range of approximately 1-25 degrees.

The system of claim 3 or 4, wherein the pressure assembly comprises spring means (15) configured to hold the first portion (14a) in an initial position using spring force.

The system of any one of claims 2-5, wherein the compression assembly comprises spring means (12, 13) configured to be biased to a spring force when the slide assembly is moved to a closed position, a resulting maximum spring force being, for example, at least 150 Newton, wherein the spring force of the spring means (12, 13) provides the force to assist movement of the slide assembly (2) from a closed position to an open position.

The system of claim 6, wherein a difference between a maximum spring force of said spring means (12, 13) and an operator threshold force required to initiate displacement of the slide assembly back in an opening direction (X) is in the range of 1-20 Newtons, for example, a range of 1-10 Newtons.

A system according to any one of the preceding claims, wherein the closing section (1a) of the guide rail (1) comprises at least one inclined portion for providing the downward displacement of the slide assembly, the pressure assembly (10) being configured to absorb a force. which is substantially proportional to a location of the slide assembly (2) relative to the inclined portion.

A system according to claim 8, wherein the inclined portion includes a non-constant angle with a horizontal plane as viewed along a horizontal direction of movement of the slide assembly, wherein the closure assembly comprises, for example, at least two inclined sections extending at mutually different angles with respect to the horizontal plane, the pressure assembly (10) being configured to generate a non-linear decreasing force during displacement of the slide assembly (2) from the closed position back to the open position, in particular such that the decrease in force is associated with the angle of the slope.

A system according to any one of the preceding claims, wherein the sliding assembly (2) is a wheeled structure (2) which is connectable to a door panel (9) wherein the wheeled structure is slidably supported on the guide rail (1), the wheeled structure being slidably supported by the pressure assembly (10) is receivable to be pressurized thereby, the wheeled structure (2) in particular comprising a force-receiving portion facing the pressing portion (10) 1s.

A system according to any one of the preceding claims, wherein the system is configured for mounting a door panel with a mass of at least 200 kg, for example at least 300 kg.

A system according to any one of claims 1-10, wherein a mass of the door panel is less than 100 kg.

A pressure assembly of a system according to any preceding claim, wherein the pressure assembly (10) in particular is configured to generate a force to assist movement of a slide assembly (2) from a closed position back to an open position after assembly. wherein the pressure assembly is at least partly movable in vertical direction relative to a mounting position, for instance a position of a respective mounting structure (14).