DOOR CLOSER WITH THROTTLE VALVE AND FLOW-DEPENDENT THROTTLE SECTION

Abstract

Door closer with a closer body (11) and in the closer body (11) a hydraulic system for at least one hydraulic function wherein the hydraulic system comprises at least one channel (13) for a hydraulic medium and at least one throttle valve (15, 17) having a throttle section (15) located in the flow path of the hydraulic medium through the channel (13), which forms a gap (21) with the channel wall (19) determining the size of the flow cross-section, characterized in that the throttle section (15) is arranged to be movable relative to the channel wall (19) in such a way that the throttle section (15) positions itself relative to the channel wall (19) under the influence of the flow.

Description

[0001] The invention relates to a door closer with a closer body and, in the closer body, a hydraulic system for at least one hydraulic function, in particular for adjusting the opening damping, closing speed and / or closing delay, wherein the hydraulic system comprises at least one channel for a hydraulic medium and at least one throttle valve which has a throttle section located in the flow path of the hydraulic medium through the channel, which throttle section forms a gap with the channel wall which determines the size of the flow cross section.

[0002] Such door closers are generally well known and are used in modern buildings to increase the safety and comfort when using building doors. The use of a hydraulic system makes it possible to equip a door closer with a wide range of functions in a simple and reliable way. These include, for example, adjusting the opening damper, the closing speed and the closing delay. In order to create a simple adjustment option for these hydraulic functions of a door closer, it is known to provide throttle valves, also known as regulating valves, in the channels of the hydraulic system. These valves are accessible on the outside of the closer body to enable the user or service personnel to make adjustments. In practice, the valves are usually located in bores in the closer body orThe valve is screwed into its housing, so that by rotating the valve using a tool, the axial position of an effective section of the valve, namely the throttle section, can be changed in order to adjust the effectiveness of the respective hydraulic function to a desired value. Such a valve is known from DE 102 28 872 A1.

[0003] The gap between the throttle section of the valve and the channel wall, also known as the throttle gap, is typically very narrow in door closers. This is because, due to their design, high pressures and low flow rates usually prevail in the hydraulic systems of door closers. Narrow throttle gaps tend to become clogged by impurities inevitably present in the hydraulic medium, which impairs functionality and endangers functional reliability. These impurities primarily include particles of various origins, material abrasion, and air bubbles. Another problem associated with throttle valves in door closers is that temperature fluctuations result in corresponding changes in the viscosity of the hydraulic medium. Oil is typically used as the hydraulic medium.At lower temperatures, the oil is more viscous than at higher temperatures, so lower temperatures result in less oil passing through the throttle gap. Consequently, in practice, temperature fluctuations due to changes in the viscosity of the hydraulic medium can, for example, lead to changes in the closing speed and also impair other hydraulic functions of the door closer. The functionality of the door, such as secure closing, can be compromised as a result.

[0004] In practice, it is found that external influences, such as the contamination of the hydraulic medium described above and temperature fluctuations resulting in changes in the viscosity of the hydraulic medium, can lead to impairments in the functionality of the door closer.

[0005] DE 92 03 872 U1 also discloses door closers filled with hydraulic fluids, which also feature a throttle valve. The throttle valve comprises a throttle body, which may have a curved profile, so that the fluid flow rate is largely independent of temperature.

[0006] A piston made of a rigid body with an elastic tip, which can be used in check or carburetor inlet valves, is known from US 3 155 367 A.

[0007] The object of the invention is therefore to eliminate these disadvantages and to create possibilities to reduce the negative effects of external influences on the hydraulic system and in particular on the throttle valves used therein in order to ensure safe and reliable operation of door closers.

[0008] This problem is solved by the features of the independent claims.

[0009] According to one aspect of the invention, the throttle section is arranged to be movable relative to the channel wall in such a way that the throttle section positions itself relative to the channel wall under the influence of the flow.

[0010] The movable throttle section according to the invention can change its position under the influence of the flow, in particular under the influence of impurities contained in the flowing hydraulic medium that are too large for the currently existing gap. It was surprisingly found that, for example, particles present in the hydraulic medium that would actually be too large for the currently set throttle gap can move the throttle section relative to the channel wall and thus locally enlarge the gap to such an extent that they can flow through the gap. The mobility of the throttle section under the influence of the flow is thus synonymous with a throttle gap that adapts itself to the flow. The invention thus creates an adaptive throttle gap.The size of the flow cross-section determined by the currently set gap does not change due to this evasive movement of the throttle section, or—depending on the geometric conditions at the gap and the nature of the throttle section's mobility—it changes minimally at most, because the gap only increases locally. At another location, the gap decreases simultaneously.

[0011] This aspect of the invention therefore makes use of the finding that a movably arranged throttle section can move relative to the channel wall under the influence of the flow, while maintaining the size of the flow cross-section but locally enlarging the gap.

[0012] As mentioned, this movement of the throttle section can cause the size of the flow cross-section to change minimally depending on the respective geometric conditions. However, such a change in the size of the flow cross-section would be so small that it would not represent a change such as can be caused by the adjustment processes mentioned above, provided the respective throttle valve is adjustable. In principle, it is possible to use non-adjustable throttle valves. The invention can also be used in conjunction with such non-adjustable throttle valves.

[0013] The inventive mobility of the throttle section relative to the channel wall under the influence of the flow is therefore not to be understood as an adjustment movement of the valve or its throttle section, such as can be carried out by a user from the outside using a tool, provided that the throttle valve has such an adjustment possibility.

[0014] Advantageous embodiments of the invention are also specified in the dependent claims, the description and the drawing.

[0015] In order for the throttle section to move and thus position itself under the influence of the flow, the throttle section is preferably designed and arranged such that it has at least one translational or rotational degree of freedom. In a preferred embodiment, the throttle section has a longitudinal axis about which the throttle section is rotationally symmetrical. If the throttle valve is adjustable, then the throttle section is preferably movable along an adjusting axis during an adjustment process, wherein this adjusting axis preferably coincides with the aforementioned axis of symmetry (longitudinal axis) of the throttle section when the throttle section is in a central basic position. The aforementioned at least one degree of freedom for self-positioning then relates to this longitudinal axis or axis of symmetry of the throttle section.

[0016] In a preferred embodiment, the throttle section does not have a translational degree of freedom for its self-positioning, but rather one, two, or three rotational degrees of freedom. With a rotationally symmetrical design of the throttle section about its longitudinal axis, it is preferably provided that the throttle section has two rotational degrees of freedom, specifically about two axes that are perpendicular to each other and to the axis of symmetry of the throttle section.

[0017] In this way, the throttle section can be inclined or tilted in any direction relative to the axis of symmetry in order to react to impurities in the flow, ie to be able to avoid particles if necessary and to position itself relative to the channel wall under the influence of the flow.

[0018] The movement of the throttle section under the influence of the flow is in particular an inclination movement, a tilting movement or a deflection movement.

[0019] As already mentioned, in some embodiments, it can be provided that, in order to adjust the size of the flow cross-section, the position of the throttle section can additionally be changed by an adjustment process. This position change for adjusting the size of the flow section is preferably a linear movement along an axis, also referred to below as the adjustment axis, with respect to which the throttle section has no degree of freedom for the self-positioning according to the invention, which takes place under the influence of the flow.

[0020] In preferred embodiments of the invention, the throttle section is movable along an adjustment axis during the adjustment process, wherein the throttle section and a channel section delimited by the channel wall taper along this adjustment axis. The throttle section and the channel section preferably have a conical shape with a circular cross-section perpendicular to the adjustment axis. In a central basic position, in which the axis of symmetry of the throttle section coincides with the adjustment axis, the throttle section and the channel wall consequently form a gap with a circular free cross-sectional area, which determines the flow cross-section of the throttle valve. In this basic position of the throttle section, a central throttle gap is therefore present.If the throttle section is moved under the influence of the flow so that its axis of symmetry no longer coincides with the control axis, the gap width increases locally, while the gap width decreases accordingly at a diametrically opposite location. Thus, local changes in the gap width occur, but the size of the flow cross-section, i.e., the free cross-sectional area of the entire gap, remains virtually unchanged.

[0021] It is preferred that the throttle section and the channel section be provided in the form of nested cones, forming the circumferential gap. However, this is not mandatory. In principle, it is possible for either only the throttle section or only the channel section delimited by the channel wall to taper, in particular to be conical.

[0022] To facilitate the introduction of contaminants present in the hydraulic medium into the gap, the channel wall and the throttle section can form an inlet opening on the upstream side that widens against the flow direction and leads into the gap. This can be achieved in a simple manner, in particular, by rounding the free end of the throttle section.

[0023] In preferred embodiments of the invention, the throttle valve comprises a base section to which the throttle section is connected and relative to which the throttle section is movable under the influence of the flow. The type of connection, which will be discussed in more detail below, is fundamentally arbitrary. In particular, the connection between the throttle valve and the base section is a movable bearing designed to allow the throttle section to self-position under the influence of the flow.

[0024] The connection can, for example, be designed in such a way that the throttle section is suspended or hooked onto the base section in such a way that it can be deflected in all directions - practically like a pendulum.

[0025] This design therefore results in a multi-part throttle valve, with the parts being movable relative to one another. The base section, relative to which the throttle section is movable under the influence of the flow, does not necessarily have to be a component of the throttle valve or be regarded as a component of the throttle valve. The base section can also form a component of the closer body or its housing or be regarded as such a component. In this case, the throttle valve can therefore be formed in one piece, namely by the movable throttle section, the movement of which occurs relative to the closer body or its housing.

[0026] Preferably, the base section has a position that determines the size of the flow cross-section, is unaffected by the flow, and can be changed by an adjustment process to adjust the size of the flow cross-section. Consequently, it is the base section that is moved during an adjustment process, with this adjustment movement of the base section being transmitted by suitable, fundamentally arbitrarily designed means to the throttle section, which, through its interaction with the channel wall, namely by forming the throttle gap, determines the free cross-sectional area of the throttle gap and thus the size of the flow cross-section.

[0027] Furthermore, it can be provided according to the invention that the throttle section is connected to the base section in a fixed or play-like manner with respect to an adjusting axis, along which the throttle section is movable for adjusting the size of the flow cross-section, and has at least one translational or rotational degree of freedom for its self-positioning in addition to this connection.

[0028] By connecting the throttle section to the base section, an adjustment movement of the base section, which is particularly performed from outside the housing by a user using a tool, can be transmitted to the throttle section. This connection does not need to be fixed or rigid with respect to the adjustment axis. A certain amount of play between the two sections along the adjustment axis is possible. Such play does not impair the precise adjustment of the flow cross-section size, but can facilitate a flexible mounting of the throttle section.

[0029] The movable arrangement of the throttle section can be such that the throttle section is freely movable relative to the base section to an extent limited only by the channel wall and the base section. This free mobility ensures that even if only comparatively small forces, such as those exerted by contaminants flowing with the hydraulic medium, are applied to the throttle section, the latter can deflect, locally enlarging the gap to allow the contaminants to pass through and thus preventing clogging of the throttle gap.

[0030] The connection between the base section and the throttle section can be a positive connection with sufficient play for the throttle section to self-position. Such a positive connection allows sufficiently free movement of the throttle section relative to the base section, allows the throttle section to be driven along when the base section is adjusted to adjust the size of the flow cross-section, and prevents the throttle section from becoming detached from the base section.

[0031] In this context, it should be noted that, at least in some hydraulic systems of door closers, at least one throttle valve must be capable of flow in both directions. Consequently, forces can act on the throttle section in both flow directions.

[0032] Against this background, the connection between the throttle section and the base section is preferably designed in such a way, in particular as a form-fitting connection, that the throttle section is arranged in a captive manner in both flow directions.

[0033] Regardless of whether the connection is a form-fit connection or not, the connection between the throttle section and the base section can include a rotary bearing with two or three rotational degrees of freedom.

[0034] The relative movement between the throttle section and the base section can in particular be a rolling movement.

[0035] Preferably, the base section and the throttle section have cooperating bearing surfaces. These bearing surfaces can be configured to form a pivot bearing with one or more rotational degrees of freedom and / or to allow a rolling motion. Preferably, one bearing surface is flat and the other bearing surface is convexly curved.

[0036] In further embodiments of the invention, the base section and the throttle section have at least two cooperating bearing surface pairs, wherein either one or the other bearing surface pair is effective depending on the direction of the flow.

[0037] The adaptive property of the throttle valve according to the invention, i.e., the ability of the throttle section to self-position under the influence of the flow to adjust the throttle gap, is thus ensured for both flow directions. The throttle valve according to the invention can therefore be flowed through by the hydraulic medium in both directions without the risk of clogging or blockage due to impurities contained in the hydraulic medium.

[0038] In further possible embodiments of the invention, the throttle section and the base section are each designed in such a way that both a positive connection and a movable bearing by interacting bearing surfaces are realized in a particularly effective manner and at the same time with ease of manufacture.

[0039] It can thus be provided that the base section and the throttle section have cooperating bearing sections, wherein one bearing section is mushroom-shaped and comprises a mushroom head provided with one or more bearing surfaces, wherein the other bearing section engages behind the mushroom head and has a receptacle for the mushroom head, which is delimited by at least one bearing surface cooperating with a bearing surface of the mushroom head.

[0040] The mushroom head, generally an extended section, on the one hand, and the bearing section engaging behind and receiving it on the other hand, therefore not only form the positive locking means for the positive connection of the throttle section and the base section, but at the same time also provide the bearing surfaces for the movable mounting of the throttle section relative to the base section.

[0041] The mushroom head can be formed on the base section and the bearing section containing the receptacle can be formed on the throttle section, or vice versa.

[0042] Preferably, the mushroom head has at least two bearing surfaces, wherein, depending on the direction of the flow, either one or the other bearing surface interacts with a bearing surface delimiting the receptacle. In particular, the mushroom head is designed as a lens or an ellipsoid. The shape of the mushroom head is selected in particular such that its bearing surfaces are comparatively slightly curved. This can be achieved, for example, by the aforementioned lens shape of the mushroom head. An appropriately dimensioned ellipsoid can also provide comparatively slightly curved bearing surfaces.

[0043] A positive connection, which also includes a certain amount of play, represents one of the preferred options for the connection or coupling between the base section and the throttle section. However, other alternative designs are also possible.

[0044] For example, according to further embodiments of the invention, the base section and the throttle section can be connected to one another by at least one elastically deformable element that allows movement of the throttle section relative to the base section under the influence of the flow. The elastically deformable element is, in particular, a separate component to which the base section and throttle section are each firmly connected. The throttle section and base section can be made of rigid or stiff, non-elastically deformable materials, for example, plastic or metal.

[0045] Alternatively, according to other embodiments of the invention, the base section and the throttle section may be directly connected to each other, wherein either the base section or the throttle section has an elastically deformable region that allows movement of the throttle section relative to the base section under the influence of the flow. It is also possible for both the base section and the throttle section to have such an elastically deformable region.

[0046] The object underlying the invention is solved according to a further aspect of the invention by the features of independent claim 19.

[0047] In particular, the throttle section is made entirely or partially from a material which, in terms of its coefficient of thermal expansion, differs from the material of the closing body in the region of the throttle section. By selecting this material, temperature fluctuations leading to changes in the viscosity of the hydraulic medium can be compensated for by the gap size and thus the size of the flow cross-section increasing or decreasing accordingly with a temperature change. At relatively lower temperatures and correspondingly more viscous oil, for example, a correspondingly larger throttle gap can be provided. For relatively thin oil, as occurs at relatively higher temperatures, a correspondingly narrower throttle gap is then automatically provided by the material selection according to the invention.

[0048] All embodiments and further developments possible above in connection with the first-mentioned aspect of the invention can, again either individually or in combination, also be provided in this further aspect of the invention.

[0049] Accordingly, the possible embodiments of this further aspect of the invention mentioned below can also be provided in conjunction with the first-mentioned aspect of the invention.

[0050] In some embodiments, it is provided that the materials differ from one another with regard to the spatial expansion coefficient or the linear expansion coefficient with respect to an adjusting axis along which the throttle section is movable for adjusting the size of the flow cross-section.

[0051] Preferably, the material of the throttle section is a plastic, wherein the material of the closing body is preferably aluminum or steel.

[0052] The invention also relates to a throttle valve for a door closer, in particular a door closer as disclosed herein, comprising a base portion and a throttle portion connected to the base portion and movable relative to the base portion.

[0053] With regard to possible further developments of this throttle valve according to the invention, reference is made to the above and following explanations, in particular to the explanations regarding the design of the throttle section, the designs of the base section and the manner of interaction between the throttle section and the base section, in particular with regard to their connection and mounting to one another.

[0054] The invention is described below purely by way of example using exemplary embodiments with reference to the drawings. These merely represent possible embodiments of the invention; further embodiments can be found in the description and the claims. They show: Fig. 1 a view of a closer body of a door closer provided with throttle valves according to the invention, Fig. 2 a throttle valve of a door closer known from the prior art, Fig. 3a and Fig. 3b schematic sectional views of a throttle valve according to the invention in a centric basic position, Fig. 4a and Fig. 4b the throttle valve of Fig. 3a and Fig. 3b with throttle section deflected relative to the basic position, Fig. 5 an enlarged partial view of a throttle section according to the invention, Fig. 6a and Fig. 6b a possible connection between the base section and the throttle section of a throttle valve according to the invention, Fig. 7 the connection according to Fig. 6a and Fig. 6b in a different relative position between throttle section and base section, Fig. 8 schematically shows the arrangement of a throttle valve according to the invention in the closing body of a door closer, Fig. 9 an alternative possibility for the connection between the throttle section and the base section of a throttle valve according to the invention, and Fig. 10 shows a further alternative possibility for the connection between the throttle section and the base section of a throttle valve according to the invention.

[0055] Fig. Figure 1 shows a generally known closer body 11 of a conventional door closer. The closer body 11 has a cuboidal basic shape with a housing 35. Fig. 1 shows a side of the housing 35 which, in the mounted state, is accessible to a user when a Fig. 1, a not-shown aperture, which may be configured, for example, as a slide, is removed. Various functional and display devices are then accessible to the user. These include, in particular, two throttle valves of a hydraulic system housed in the closer body 11. Of these throttle valves, also referred to as regulating valves, which are screwed into the closer body 11, two components, referred to here as base sections 17, are accessible. These are also referred to as the valve head and can be adjusted using a screwdriver.

[0056] Fig. Figure 2 shows a throttle valve of a conventional door closer known from the prior art. The aforementioned base section 17 is provided with a slot 17a for a screwdriver on its end face, which is accessible from the outside when screwed in. Furthermore, the base section 17 has a thread 39, via which the base section 17, and thus the entire throttle valve, is screwed into an opening 12 formed in the closer body 11.

[0057] At its end facing away from the end face with the slot 17a, the throttle valve is provided with a conical throttle section 15, which is arranged in a channel section 25 of a channel of the door closer's hydraulic system in order to regulate the flow of a hydraulic medium in the form of oil through the channel. The arrows S indicate the flow direction of the hydraulic medium. In principle, however, it is possible for the channel to flow in the opposite direction. In this case, too, the flow can be regulated by the throttle valve 15, 17.

[0058] In the area of the throttle section 15 of the valve, the channel is also conical, wherein the conical throttle section 15 and the conical channel section 25 have the same cone angle and consequently the throttle section 15 forms with the wall 19 of the channel section 25 a circumferential throttle gap 21, the width of which is constant along a central axis 15a of the valve 15, 17.

[0059] The size of the gap 21 determines the size of the flow cross-section in the channel section 25 set by the respective position of the throttle valve 15, 17 in the opening 12 and thus determines the corresponding volume flow of the hydraulic medium.

[0060] The volume flow can be regulated by changing the position of the valve 15, 17. Using a screwdriver, the user can adjust the valve 15, 17 further into the opening 12 or in the opposite direction via the thread 39, along an adjustment axis 23, which here coincides with the central axis 15a of the valve 15, 17.

[0061] This axial adjustment movement changes the size of the gap 21 between the two conical surfaces, ie between the conical outer surface of the throttle section 15 on the one hand and the conical inner wall of the channel section 25 on the other hand.

[0062] As already mentioned in the introduction, the gap 21 can become clogged by impurities in the hydraulic medium, for example by particles 37, indicated schematically here as circles, which are too large to pass through the gap 21.

[0063] The embodiments of a throttle valve according to the invention described below differ from this known throttle valve in that the throttle section 15 and the base section 17 are not integrally or rigidly connected to one another, but rather that the throttle section 15 is movable relative to the base section 17. All the above statements regarding the closing body apply here accordingly, ie the invention can be used without changing the closing body. In other words, existing known throttle valves, as described for example in Fig. 2, can be replaced by throttle valves according to the invention without having to modify the closing body.

[0064] The Fig. 3a and Fig. 3b, Fig. 4a and Fig. 4b and Fig. 5 illustrate the basic principle of the invention. Possible connections, which can also be referred to as couplings or bearings, or as comprising couplings or bearings, between the throttle section 15 and the base section 17, which enable the mobility of the throttle section 15 relative to the base section 17, are explained elsewhere with reference to further figures.

[0065] The Fig. 3a and Fig. 3b, the latter showing a section perpendicular to the central axis 15a of the throttle section 15, shows that in the central basic position of the throttle section 15 shown here, a central throttle gap 21 is present. The width of this gap 21 is therefore constant in the circumferential direction around the central axis 15a.

[0066] Particles 37 whose diameter is larger than the gap width cannot therefore flow through the gap 21.

[0067] The inventive mobility of the throttle section 15 enables the throttle section 15 to be deflected under the influence of the flow, in this case by the particles 37 flowing with the hydraulic medium, so that the throttle section 15 is tilted and the central axis 15a is inclined to the adjusting axis 23. As Fig. 4a and Fig. As shown in Figure 4b, this results in a local increase in the gap width, i.e., an enlarged gap area 22 is created at one circumferential angle. At the diametrically opposite point, the gap width is reduced accordingly. Overall, this creates a so-called eccentric throttle gap.

[0068] As a result of this deflection of the movable throttle section 15, the particles 37 carried by the hydraulic medium have, in a sense, made their own way through the gap 21, namely through the gap area 22 which they themselves have enlarged.

[0069] As explained in the introduction, the size of the flow cross-section remains constant, ie the free cross-sectional area of the gap 21 does not change in terms of its size, but in terms of its shape.

[0070] Fig. 5 shows that the free end of the throttle section 15 can be rounded, whereby an outwardly widening, annular introduction opening 27 is present in the gap 21, which makes it easier for particles 37 or other contaminants of the hydraulic medium to enter the gap 21 and deflect the throttle section 15.

[0071] A possibility for the movable mounting of the throttle section 15 on the base section 17 is shown in the Fig. 6a and Fig. 6b and Fig. 7. The throttle section 15 and the base section 17 are positively connected to one another by two bearing sections which are rotationally symmetrical with respect to the central axis 15a, namely by a mushroom-shaped bearing section 29 of the base section 17 and a bearing section of the throttle section 15 which comprises a receptacle 31 for the mushroom head 29 and a stop section 32 which encompasses the mushroom head 29.

[0072] On its end face facing the throttle section 15, the mushroom head 29 is provided with a comparatively slightly curved bearing surface 29a, which interacts with a flat bearing surface 31a extending perpendicular to the central axis 15a and delimiting the receptacle 31.

[0073] When hydraulic medium flows through the channel section and the so-called throttle pressure D moves the throttle section 15 toward the base section 17, thus bringing the aforementioned bearing surfaces 29a and 31a into contact with one another, the mushroom head 29 can roll on the flat bearing surface 31a of the throttle section 15 if a torque or tilting moment acts on the throttle section 15. Since the positive connection between the throttle section 15 and the base section 17 has sufficient play, the throttle section 15 is practically freely movable relative to the base section 17, so that even comparatively small forces or moments are sufficient to deflect the throttle section 15. This possibility for self-alignment or self-positioning of the throttle section 15 under the influence of the flow is facilitated by the described design of the bearing surfaces 29a, 31a.

[0074] For a flow direction S as in Fig. 3a and Fig. 4a, so if the mentioned throttle pressure D is in the position shown by the arrow in Fig. 6a, a further pair of bearing surfaces formed by the throttle section 15 and the base section 17 is not effective as a bearing for the movement of the throttle section 15 relative to the base section 17.

[0075] This further pair of bearing surfaces is formed by an annular surface 31b on the stop section 32 of the throttle section 15 on the one hand and by an annular surface 29b on the mushroom head 29, these surfaces 31b, 29b each being rotationally symmetrical with respect to the central axis of the base section 17 or the central axis 15a of the throttle section 15 coinciding with the adjusting axis 23.

[0076] How Fig. 6b, in which a position of the throttle section 15 tilted relative to the base section 17 is shown, the surface 31b of the stop section 32 strikes the surface 29b of the mushroom head 29 in order to limit the movement of the throttle section 15.

[0077] Fig. 7 shows that the positive connection between the throttle section 15 and the base section 17 has a slight play in the direction of the adjusting axis 23, because the bearing surfaces 29a, 31 are slightly spaced from each other here.

[0078] If the throttle section 15 and the base section 17 are acted upon in such a way that they diverge, for example during an adjustment process acting on the base section 17 or during flow in one of the directions S (cf. Fig. 3a and Fig. 4a) opposite direction, the mushroom head 29 serves as a driver for the throttle section 15 or to hold the throttle section 15.

[0079] In these cases, the two bearing surfaces 29b, 31b abut one another. The surfaces 29b, 31b are designed such that—relative to a plane perpendicular to the adjusting axis 23—a comparatively flat or small stop angle α is present. This ensures secure driving or secure holding, i.e., it is ensured that the mushroom head 29 cannot escape from the receptacle 31. This design of the bearing surfaces 29b, 31b also ensures that the throttle section 15 cannot jam on the mushroom head 29.

[0080] The surfaces 31a, 31b of the mushroom head 29 can have at least approximately the same, comparatively small curvature, so that the mushroom head 29 has a lens-shaped basic shape.

[0081] In this way, the movability of the throttle section 15, which enables self-positioning under the influence of the hydraulic flow, can be ensured for both flow directions.

[0082] The above-described design of the interacting surfaces thus ensures free movement of the throttle section 15 relative to the base section, requiring only minimal forces or moments. The influence of the flow of the hydraulic medium, in particular the influence of impurities contained in the hydraulic medium, is sufficient to generate such forces or moments.

[0083] Fig. 8 shows a throttle valve according to the invention over its entire axial extent, wherein the throttle section 15 is shown in a tilted position relative to the base section 17, in which the throttle gap has an enlarged gap area 22.

[0084] As already mentioned elsewhere, the closer body 11 or its housing, at least in the area of the throttle section 15, and the throttle section 15 can be made of different materials that differ from one another in terms of their thermal expansion coefficients. The closer body 11 is made, for example, of steel or aluminum, while the throttle section 15 is made of a plastic. In the event of temperature fluctuations, the dimensions of the throttle section 15 thus change to a greater extent than those in the area of the closer body 11 that delimits the throttle gap 21. At lower temperatures, the throttle gap 21 is therefore larger than at higher temperatures. The material can be selected in such a way that precisely the size differences are created that compensate for a change in the viscosity of the hydraulic medium that is also caused by temperature fluctuations.

[0085] Fig. 9 shows an alternative embodiment of the connection between the throttle section 15 and the base section 17. The throttle section 15 is provided here with an elastically deformable region 33, via which the throttle section 15 is firmly connected to the base section 17. This deformable region 33 enables the mobility of the throttle section 15 relative to the base section 17, indicated by the double arrow B. The region 33 can be cylindrical with a circular cross-section around the central axis 15a of the throttle section 15, so that it can be deflected in any direction, i.e. regardless of the circumferential angular range around the central axis 15a at which contamination penetrates into the gap, this can cause a deflection of the throttle section 15.

[0086] Fig. 10 again shows a form-fitting connection with sufficient play between the throttle section 15 and the base section 17, which ensures the mobility of the throttle section 15 relative to the base section 17 in all directions, indicated by a double arrow B. Unlike in the embodiment of the Fig. 6a, Fig. 6b and Fig.7, however, the front end of the mushroom head 29 is flat. Thus, there is no rolling movement between the base section 17 and the throttle section 15. Instead, the circumferential contact surface 31c on the front side of the stop section 32 of the throttle section 15 is beveled, i.e., it does not run perpendicular to the central axis 15a of the throttle section 15, so that when flow passes through the valve, the throttle section 15 is pressed against the surface 29c of the base section 17. Due to the aforementioned bevel, the throttle section 15 can be tilted if contamination of the hydraulic medium exerts a force or moment in the area of its free end (not shown here).

[0087] A further advantage of the invention in all described embodiments is that the mobility of the throttle section 15 means that contaminants, for example, in the form of air pockets, cannot become statically trapped. In particular, it has been found that the flow of the hydraulic medium can cause the throttle section 15 to vibrate, thereby "shaking off" particulate contaminants and dissolving air pockets.

[0088] Consequently, according to the invention, the throttle section 15, which is movable under the influence of the flow, can not only allow larger contaminants to pass through the throttle gap 21, but can also ensure that smaller particles, which could pass through the throttle gap 21 even without the throttle section 15 being movable, cannot become lodged in the throttle gap 21. List of reference symbols 11 closer body 12 Opening 13 Channel 15 Throttle section 15a Central axis 17 Base section 17a slot 19 Canal wall 21 gap 22 enlarged gap area 23 Adjustment axis 25 canal section 27 Insertion opening 29 Mushroom Head 29a Storage area 29b Storage area 29c contact surface 31 recording 31a Storage area 31b Storage area 31c contact surface 32 Annex section 33 elastically deformable area 35 housings 37 particles 39 threads S Flow direction D Throttle pressure B Movement of the throttle section A Adjustment direction α stop angle

Claims

[1] Door closer with a closer body (11) and in the closer body (11) a hydraulic system for at least one hydraulic function wherein the hydraulic system comprises at least one channel (13) for a hydraulic medium and at least one throttle valve (15, 17) having a throttle section (15) located in the flow path of the hydraulic medium through the channel (13), which forms a gap (21) with the channel wall (19) determining the size of the flow cross-section, characterized by , that the throttle section (15) is arranged to be movable relative to the channel wall (19) in such a way that the throttle section (15) positions itself relative to the channel wall (19) under the influence of the flow. [2] Door closer according to claim 1, characterized by that the throttle section (15) does not have a translational degree of freedom for its self-positioning, but rather one, two or three rotational degrees of freedom. [3] Door closer according to claim 1 or 2, characterized by that in order to adjust the size of the flow cross-section, the position of the throttle section (15) can additionally be changed by an adjustment process. [4] Door closer according to claim 3, characterized by that the throttle section (15) is movable along an adjusting axis (23) during the adjustment process. [5] Door closer according to one of the preceding claims, characterized by that the channel wall (19) and the throttle section (15) form an inlet opening (27) on the inflow side which widens against a flow direction (S) and leads into the gap (21). [6] Door closer according to one of the preceding claims, characterized by that the throttle valve (15, 17) or the closing body (11) comprises a base section (17) to which the throttle section (15) is connected and relative to which the throttle section (15) is movable under the influence of the flow. [7] Door closer according to claim 6, characterized by that the base section (17) has a position which determines the size of the flow cross-section and is uninfluenced by the flow, which position can be changed by an adjustment process in order to adjust the size of the flow cross-section. [8] Door closer according to claim 6 or 7, characterized by that the throttle section (15) is connected to the base section (17) in a fixed or play-like manner with respect to an adjusting axis (23) along which the throttle section (15) is movable to adjust the size of the flow cross-section, and has at least one translational or rotational degree of freedom for its self-positioning in addition to this connection. [9] Door closer according to one of claims 6 to 8, characterized by that the throttle section (15) is freely movable relative to the base section (17) to an extent limited only by the channel wall (19) and the base section (17). [10] Door closer according to one of claims 6 to 9, characterized by that the connection between the base section (17) and the throttle section (15) comprises a positive connection which has a play sufficient for the self-positioning of the throttle section (15). [11] Door closer according to one of claims 6 to 10, characterized by that the connection between the base section (17) and the throttle section (15) comprises a rotary bearing with two or three rotational degrees of freedom. [12] Door closer according to one of claims 6 to 11, characterized by that the relative movement between the throttle section (15) and the base section (17) is a rolling movement. [13] Door closer according to one of claims 6 to 12, characterized by that the base section (17) and the throttle section (15) have cooperating bearing surfaces, one bearing surface being flat and the other bearing surface being convexly curved. [14] Door closer according to one of claims 6 to 13, characterized by that the base section (17) and the throttle section (15) have at least two cooperating pairs of bearing surfaces, wherein either one or the other pair of bearing surfaces is effective depending on the direction (S) of the flow. [15] Door closer according to one of claims 6 to 14, characterized by in that the base section (17) and the throttle section (15) have cooperating bearing sections, wherein one bearing section is mushroom-shaped and comprises a mushroom head (29) provided with one or more bearing surfaces (29a, 29b, 29c), wherein the other bearing section engages behind the mushroom head and comprises a receptacle (31) for the mushroom head (29), which receptacle is delimited by at least one bearing surface (31a, 31b, 31c) cooperating with a bearing surface (29a, 29b, 29c) of the mushroom head (29). [16] Door closer according to claim 15, characterized bythat the mushroom head (29) has at least two bearing surfaces (29a, 29b), wherein, depending on the direction (S) of the flow, either one or the other bearing surface interacts with a bearing surface (31a, 31b) of the throttle section (15), wherein the mushroom head (29) is preferably lens-shaped or designed as an ellipsoid. [17] Door closer according to one of claims 6 to 16, characterized by that the base section (17) and the throttle section (15) are connected to one another by at least one elastically deformable element which allows movement of the throttle section (15) relative to the base section (17) under the influence of the flow. [18] Door closer according to one of claims 6 to 16, characterized bythat the base section (17) and the throttle section (15) are directly connected to one another, wherein the base section (17) and / or the throttle section (15) have an elastically deformable region (33) which allows movement of the throttle section (15) relative to the base section (17) under the influence of the flow. [19] Door closer according to claim 1, characterized by that the throttle section (15) is made entirely or partially from a material which differs in terms of the thermal expansion coefficient from the material of the closing body (11) in the region of the throttle section (15). [20] Door closer according to claim 19, characterized by that the materials differ from one another with regard to the spatial expansion coefficient or the linear expansion coefficient with respect to an adjusting axis (23) along which the throttle section (15) is movable for adjusting the size of the flow cross-section. [21] Door closer according to claim 19 or 20, characterized by that the material of the throttle section (15) is a plastic, wherein the material of the closing body (11) is preferably aluminum or steel. [22] Throttle valve (15, 17) for a door closer according to one of the preceding claims, comprising a base portion (17) and a throttle portion (15) connected to the base portion (17) and movable relative to the base portion (17).

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