Hydraulically coupled sleeve

Abstract

The invention discloses a hydraulic coupling sleeve for coupling with a hydraulic coupling plug, the coupling sleeve having a coupling housing and a sleeve body which is movable in the coupling housing and can be actuated for closing or opening the coupling, the sleeve body having a plug chamber for at least partially receiving and for fluidly connecting the coupling plug, a supply chamber for fluidly connecting with an external supply channel, a low-pressure chamber for fluidly connecting with a pressure medium tank, and an inner chamber fluidly connected with the supply chamber, wherein a supply-seat valve device is provided, by actuation of which a supply flow path can be configured between the supply chamber and the plug chamber, and wherein a load-unload seat valve device is provided, by mechanical actuation of which a pressure unloading of the inner chamber towards the low-pressure chamber is possible and by hydraulic actuation of which depending on the pressure in the inner chamber a pressure limitation in the inner chamber is possible.

Description

TECHNICAL FIELD

[0001] The present application relates to a hydraulic coupling sleeve for use with a hydraulic coupling plug. BACKGROUND

[0002] Coupling sleeves of this type are used for connecting and disconnecting hydraulic pressure medium lines quickly and without leakage. The coupling sleeves are arranged, for example, at valve blocks or control blocks and are connected to a matching hydraulic coupling plug with the corresponding pressure medium line when required. The coupling sleeve basically has a coupling housing and a sleeve body which is moveable in the coupling housing and can be actuated. Two seat valves are configured in the sleeve body, wherein one seat valve controls the pressure medium connection of a (usually transverse) supply channel to a plug receptacle, and wherein the other seat valve controls the pressure medium connection of a supply chamber to a pressure medium groove. If the plug receptacle for accommodating the hydraulic coupling plug is released, the last-mentioned seat valve is actuated when the sleeve body is actuated, so that the pressure inside the sleeve body is unloaded. The actuation and control of the seat valve mentioned at the beginning is thus achieved mechanically by inserting the coupling plug.

[0003] The disadvantage of this coupling sleeve is that if both seat valves are closed and the supply chamber is closed at the rear, for example, by a control valve, the pressure medium is enclosed in the sleeve body. If this then leads to a temperature increase, the pressure in the inner chamber of the sleeve body can rise sharply and cause damage or malfunctions.

[0004] From DE 10 2009 034 616 A1 a coupling sleeve is thus known which has a pressure-limiting valve integrated in the sleeve housing, through which the pressure rise is limited.

[0005] The disadvantage of this is the construction form of the coupling sleeve, since the integrated pressure-limiting valve is arranged next to the other functional axes of the coupling sleeve in a complex manner.

[0006] The solution of the publication DE 10 2014 209 278 A1 integrates a pressure-limiting valve into the functional shaft of the coupling sleeve. Here, the aforementioned second seat valve not only assumes the above-mentioned pressure relief upon mechanical release of the coupling, but also assumes the pressure limitation in the inner chamber. For both functions, only one valve body with the associated valve seat is provided. The valve body can be mechanically actuated upon actuation of the sleeve body and can be hydraulically actuated depending on the pressure difference between the inner pressure and the low pressure. Here, the valve body is designed as a hollow body or sleeve, wherein the sleeve protrudes from the sleeve body for mechanical actuation and has precisely manufactured area differences at the outer circumference for its hydraulic actuation, by which the pressure in the inner chamber acts in the opening direction. In the case of the two functions of pressure relief and pressure limitation, which can be precisely implemented, the manufacture of the valve body is challenging. SUMMARY

[0007] In contrast thereto, the task of the present application is to realize a coupling sleeve with pressure relief and pressure limitation functions, which can be simply manufactured.

[0008] The task is solved by a coupling sleeve according to the application. The refinements of the application are explained in the description.

[0009] A hydraulic coupling sleeve for coupling with a hydraulic coupling plug has a coupling housing and a displaceably operable sleeve body in the coupling housing for closing or opening the coupling. Both are preferably sleeve-shaped. The coupling sleeve has, inter alia, a plug chamber for accommodating the coupling plug at least section-wise on the front side, a supply chamber, in particular transversely, for fluid connection with an external supply channel, and a low-pressure chamber, in particular on the rear side, for fluid connection with a pressure medium tank or reservoir. The supply chamber is connected in a fluid manner with an inner chamber of the coupling sleeve. A supply-seat valve device is provided, which can be operated and controlled mechanically, in particular by the coupling of the coupling sleeve with the coupling plug or the insertion of the coupling plug into the plug chamber. Here, a supply flow path can be configured by such an operation between the supply chamber and the plug chamber. Furthermore, a load-unloading-seat valve device is provided, by operation of which, in particular mechanical operation, the inner chamber can be pressure-unloaded towards the low-pressure chamber, and by a further operation of the load-unloading-seat valve device depending on the pressure in the inner chamber, in particular hydraulic operation, the pressure in the inner chamber can be limited. According to the invention, the load-unloading-seat valve device has, for the pressure-unloading mentioned, an in particular mechanically operable valve body with an associated valve seat and, separately therefrom, for the pressure limitation, a further, according to the pressure in particular hydraulically operable valve body with an associated valve seat. They are arranged coaxially or at least substantially coaxially. "Substantially coaxially" is met in the sense of the present text when the valve seats and valve bodies are arranged radially within an envelope surface which can be spanned by the outer contour of the largest valve body among the valve bodies in its operating direction.

[0010] The pressure-unloading function and the pressure-limiting function are thus composed of two separate seat valves of the load-unloading-seat valve device and thus of valve bodies and valve seats which can be manufactured independently of one another. The coaxial arrangement is advantageous in terms of construction space technology and function. The design and manufacture of the individual functions, i.e. pressure-unloading and pressure-limiting, are thus simplified.

[0011] In particular, the coupling sleeve has a concentric or coaxial structure with regard to its components which can move relative to one another, such as valve bodies, valve seats, springs and / or the like, from the low-pressure chamber towards the plug chamber.

[0012] In an improvement, the mechanically operable valve body of the supply-seat valve device and the valve seat associated with it are arranged coaxially with the components mentioned so far.

[0013] In an embodiment, the valve bodies of the load-unloading seat valve device have oppositely arranged actuating directions. Preferably, one, in particular mechanically actuatable, valve body of the load-unloading seat valve device can be actuated into the sleeve body and the other, in particular hydraulically actuatable, valve body can be actuated in the oppositely arranged direction. It is thereby possible that both are loaded into their valve seats by the same spring, in particular a pressure spring.

[0014] If, in an embodiment, the valve seats of the load-unloading seat valve device are constantly spaced apart, in particular fixedly connected, this is also simplified.

[0015] In an embodiment, the first spring is a pressure spring by which the two valve bodies of the load-unloading seat valve device are coupled and loaded into their respectively assigned valve seats. The first spring can be an elastomer, a coil spring or a gas spring or the like, wherein a coil spring is provided for reasons of standardization, reliability and expenditure in terms of equipment technology.

[0016] In a preferred embodiment, the two valve bodies of the load-unloading seat valve device are individually loaded into their respectively assigned valve seats by the first spring. A further spring is thus not provided, for example only one of the two valve bodies is loaded by this spring and the other is not.

[0017] The first spring is in a variant configured as a first spring group with a plurality of spring elements coupled in parallel or in series.

[0018] In an embodiment, the valve seat of the mechanically actuatable valve body of the supply seat valve device and the further, in particular hydraulically actuatable, valve body of the load-unloading seat valve device are coupled by a second spring and loaded in their respective closing direction.

[0019] The second spring is in a variant configured as a second spring group with a plurality of spring elements coupled in parallel or in series.

[0020] In an embodiment, the in particular mechanically actuatable valve body of the load-unloading seat valve device and the valve body of the supply seat valve device have oppositely arranged actuating directions.

[0021] In an embodiment, the in particular mechanically actuatable valve body of the load-unloading seat valve device is completely sunk or arranged within the sleeve body at least in the fully actuated case.

[0022] In an embodiment, the two valve bodies of the load-unloading seat valve device are at least partially sectionally jointly arranged and guided in the guide sleeve, in particular in series, on the basis of the coupling by the first spring.

[0023] The guide sleeve is in one refinement can-shaped, wherein a valve body of the load dump-seat valve arrangement, in particular mechanically actuatable, projects from the can opening of the guide sleeve and has there preferably an actuation section.

[0024] The guide sleeve is in one refinement can-shaped, wherein a valve seat of a further valve body of the load dump-seat valve arrangement, in particular hydraulically actuatable, is configured at the can bottom of the guide sleeve, which can bottom is penetrated by a first throttle bore in the direction of the inner chamber from the mentioned valve seat. The further valve body of the load dump-seat valve arrangement is then loaded by the pressure in the inner chamber and can limit the pressure by the release of the valve seat of this valve body.

[0025] Preferably, a second throttle bore is connected from the inner chamber before the first throttle bore. The pressure medium flow resulting in the case of a hydraulically actuatable valve body can then be limited in a targeted manner.

[0026] In one refinement, the sealing section of the further valve body of the load dump-seat valve arrangement, in particular hydraulically actuatable, is a solid body, in particular a ball or a cone or at least one ball section or cone section.

[0027] In one refinement, the valve body is at least partially section-wise metallic and / or made of plastic.

[0028] In one refinement, the valve body of the load dump-seat valve arrangement, in particular mechanically actuatable, is a hollow body, in particular a sleeve with a through recess.

[0029] In one refinement thereof, the sealing section of the valve body of the load dump-seat valve arrangement, in particular mechanically actuatable, is a radial enlargement on the outer circumference at the valve body.

[0030] In one refinement, a pressure-limiting-pressure medium flow path from the inner chamber via the valve seat assigned to the further valve body of the load dump-seat valve arrangement and through the valve body of the load dump-seat valve arrangement, in particular mechanically actuatable, towards the low-pressure chamber can be configured when the further valve body of the load dump-seat valve arrangement is hydraulically actuated.

[0031] In one refinement, a load-dump-pressure medium flow path from the inner chamber via the valve seat assigned to the valve body of the load dump-seat valve arrangement towards the low-pressure chamber can be configured when the valve body of the load dump-seat valve arrangement is mechanically actuated. The inner chamber can then be load dumped independently of the pressure-limiting function, in particular during the mechanical actuation of the sleeve body for releasing the coupling and / or the coupling plug.

[0032] In an improvement, the diameter of the first spring is greater than the diameter of the sealing section of the hydraulically actuatable valve body. In order to be able to support the first spring at the sealing section, in an improvement a support section separate from or integral with the sealing section is provided, against which the end section of the first spring bears. The support section thus transmits the force between the sealing section and the first spring.

[0033] The support section is guided in the guide sleeve with a clearance in device technology. Here, the clearance is chosen such that buckling is prevented.

[0034] In an improvement, the edges of the support section are rounded or chamfered towards the inner peripheral side of the guide sleeve in order to prevent buckling.

[0035] In a preferred improvement, the clearance of the support section in the guide sleeve on the edge side, the height of the support section in the actuating direction, the treatment of the edges of the support section and / or the treatment of the inner peripheral side of the guide sleeve are coordinated such that buckling of the support section in the guide sleeve is prevented. BRIEF DESCRIPTION OF DRAWINGS

[0036] Three embodiments of a coupling sleeve according to the application are explained in more detail below in the drawings. Therein:

[0037] Figure 1 A coupling sleeve according to a first embodiment is shown in a longitudinal sectional view, which is placed in a valve block;

[0038] Figure 2 Details of the pressure-limiting function of a coupling sleeve according to Figure 1 are shown;

[0039] Figure 3 A variant of the pressure-limiting function according to a second embodiment is shown, and

[0040] Figure 4 A variant of the pressure-limiting function according to a third embodiment is shown. DETAILED DESCRIPTION

[0041] A coupling sleeve according to Figure 1A hydraulic coupling sleeve 1 according to the application is accommodated in a valve block 2. It is also possible to use it at the housing of a hydraulic aggregate, a tank, a hydraulic coupling of a mobile working machine or the like. The coupling sleeve 1 has a coupling housing 4 which is fixedly connected to the valve block 2. The coupling housing 4 is designed substantially cylindrically and sleeve-shaped and is accommodated with its outer periphery in a cylinder bore 6 of the valve block 2 and is seated there axially. A two-part, mainly sleeve-shaped sleeve body 8 is axially movably guided in the coupling housing 4 along a central axis 10 of the coupling sleeve 1. A first part 12 of the sleeve body 8 has an outwardly open plug chamber 14 for accommodating at least sectionally a coupling plug (not shown) in the region of the coupling housing 4. The first part 12 is connected to a second part 16 of the sleeve body 8 away from the plug chamber 14. The second part 16 is designed as an Überwurfhülse which in the shown embodiment is screwed with the first part 12.

[0042] The first part 12 has in the region of the plug chamber 14 for example through recesses 18 which are constructed completely star-shaped distributed and respectively open radially outwardly conically, in which respectively a latching ball 20 is accommodated. The radial travel of the latching balls 20 is inwardly limited by a conical tapering and outwardly by the inner peripheral side of the sleeve housing 4, independently of the axial position of the sleeve body 8. Here, the inner peripheral side is provided with a variable radius in axial direction, whereby the latching balls 20 obtain more radial outward travel when the sleeve body 8 is axially operated in the direction toward the plug chamber 14. A release of the coupled, or respectively latched, coupling plug is thereby produced. For further explanations, reference is made in this regard for the purposes of disclosure to the applicant's publication DE 10 2014 209 278 A1.

[0043] The coupling sleeve 1 has on the distal side or opposite to the axial direction of the plug chamber 14 a low-pressure chamber 22 which is in pressure medium connection with a pressure medium tank, for example with a reservoir. Further explanations are also dispensed with here and reference is made for the purposes of disclosure to the applicant's publication DE 10 2014 209 278 A1.

[0044] The first part 12 has for example centrally with respect to the axis 10 a supply chamber 24 which points radially outwardly and is fluidically connected to an inner chamber 28 of the sleeve body 8 by a star-shaped constructed radial-axial bore 26.

[0045] At the first component 12 a supply valve seat 30, hereinafter referred to as second valve seat 30, is configured, against which a pot-shaped valve body 32, hereinafter referred to as second valve body 32, can come to bear. The second valve body 32 is loaded against the second valve seat 30 by means of a second spring 34. By means of the thus configured seat valve 30, 32 a supply-pressure medium flow path from the supply chamber 24 via the second valve seat 30 into the plug chamber 14 can be controlled or configured.

[0046] Furthermore, the coupling sleeve 1 has at its end section with the low-pressure chamber 22 a load-unloading seat valve device 36, by means of the mechanical actuation of which in the present embodiment a pressure unloading of the inner chamber 28 is achieved and by means of the hydraulic actuation of which depending on the pressure pi in the inner chamber 28 a limitation of the pressure pi is achieved. For the pressure unloading the load-unloading seat valve device 36 has a mechanically actuatable valve body 38, hereinafter referred to as first valve body 38, and at the second component 16 a valve seat 40, hereinafter referred to as first valve seat 40, is assigned to the first valve body. The mechanical actuation of the load-unloading seat valve device can be effected, for example, by means of a Figure 1 The left-hand projection (shown in bold lines) effects and causes a displacement of it to the right in Figure 1 until the projection strikes against the second component 16 (shown in thin lines). A continued actuation by means of the projection then causes a displacement of the sleeve body 8 to the right in Figure 1 and thus a release of the coupling for the purpose of accommodating or releasing a coupling plug. Reference is made to the disclosure of the applicant's publication DE 12014 209 278 Al for this process.

[0047] The first valve body 38 is penetrated by a through-going bore 42 coaxial to the central axis 10 and has on its length, for example, one third and two thirds, a flange 44 and 46, respectively, on the outer periphery. Here, the flange 44 carries a sealing section or sealing face against which the first valve seat 40 can come to bear. The other flange 46 is designed as a guide flange, wherein the first valve body 38 is guided axially movably therein by means of this flange in a pot-shaped guide sleeve 48. Here, the first valve body 38 projects out of the pot opening of the guide sleeve 48 and beyond the flange 44 with an end section by means of an outer toothing is guided axially movably in the second component 16. The first valve body 38 is supported in the guide sleeve 48 in the direction of the pot bottom 50 of the guide sleeve 48 by means of a first spring 52 embodied as a pressure spring. Further explanations are first made in accordance with Figure 2 the longitudinal section.

[0048] Figure 2 is shown in a longitudinal sectionFigure 1 Detail A as specified. The bottom 50 of the tank is in accordance with Figure 2 A valve body 56, referred to below as a third valve body 56, is inserted into the radially expanding end section pointing towards the first spring 52, and is hydraulically actuated. In the illustrated embodiment, this third valve body is constructed as a solid, metallic, and spherical structure. A plate 58 is held against the bottom 50 of the tank by the first spring 52, and is guided with clearance at the inner circumferential side 60 of the guide sleeve 48 on its outer periphery. The plate 58 covers the radially expanding end section of the stepped hole 54 pointing towards the first spring 52, in which the third valve body 56 is arranged. The third valve body abuts against the plate 58. The third valve body 56 is loaded in a valve seat 62, referred to below as a third valve seat 62, by the first spring 52, thereby... Figure 1 The low-pressure chamber 22 is blocked in a fluid manner from the inner chamber 28.

[0049] According to this embodiment, the guide sleeve 48 is pressed into a similarly can-shaped cover sleeve 64 at its canister section. The cover sleeve 64 has, at its bottom, a throttle valve orifice 66 penetrating the canister bottom of the cover sleeve 64, adjacent to and coaxial with the stepped orifice 54 of the guide sleeve 48. Figure 1 The pressure medium connection between the storage tank chamber 22 and the inner chamber 28 can therefore be achieved solely through the throttle valve orifice 66 and when the third valve body 56 disengages from the third valve seat 62.

[0050] In an alternative (not shown), the tank bottom of the cover sleeve 64 is closed, meaning it does not have such a throttling valve orifice, and the guide sleeve 48 is accommodated within the tank-shaped cover sleeve 64 with a predetermined clearance using its tank section. The gap between these tank sections, resulting from the clearance, constitutes a throttling gap through which the tank chamber 22 can be fluidly connected to the inner chamber 28. Through this throttling gap, the pressure medium fluidly connected to the inner chamber 28 is present at the third valve body 56. When this third valve body disengages from its third valve seat 62, the aforementioned fluid connection from the inner chamber 28 to the tank chamber 22 is established.

[0051] When coupling and releasing the coupling device with the hydraulic coupling plug, further description of the function of the coupling sleeve 1 is omitted here, and the disclosure of publication DE 10 2014 209 278 A1 is consulted again. The following description will only cover the basic state and operation of the coupling sleeve 1, which is essential for understanding the present invention.

[0052] Figure 1The basic state of the coupling sleeve 1 is shown, in which the coupling plug is not coupled and the plug chamber 14 is therefore free. Furthermore, the mechanically actuated first valve body 38 and the hydraulically actuated second valve body 56 of the load unloading-seat valve device 36 are not actuated. These two valve bodies 38 and 56 are arranged according to... Figure 2 Therefore, it is located in its associated valve seat 40 or 62. Therefore, regarding the pressure pI in the inner chamber 28, neither pressure relief nor pressure limiting is performed.

[0053] Furthermore, it is assumed that a supply pressure pV exists in supply chamber 24. Further, it is assumed that supply chamber 24 is subsequently shut off by a control valve (not shown). Therefore, according to... Figure 1 The inner chamber 28 is pressure-sealed according to Figure 2 At the first valve seat 40 and the third valve seat 62 and according to Figure 1 The pressure is cut off at the second valve seat 30. The volume of the included pressure medium is subjected to thermal fluctuations and therefore changes in its density. Correspondingly, the pressure pI in the inner chamber 28 also changes. In the illustrated embodiment, this pressure exists at the end of the hydraulically actuated third valve body 56 of the load unloading-seat valve device 36 via the throttle orifice 66 and the stepped orifice 54. This also applies to the aforementioned alternative in the absence of the mentioned throttle orifice, in which case the pressure pI exists between the guide sleeve 48 and the cover sleeve 64 via the gap mentioned above. If the pressure pI now exceeds according to Figure 1 , 2 The pressure equivalent of the first spring 52, then the third valve body 56 from according to Figure 2 The third valve seat 62 disengages and forms a portion from the valve seat in the illustrated embodiment according to the valve seat 62. Figure 1 The supply chamber 24 is connected to the inner chamber 28 via a radial orifice 26 and from there to the low-pressure chamber 22 via a throttle valve orifice 66, a stepped orifice 54, and a through recess 42. Correspondingly, the pressure medium is released from the inner chamber 28, and the pressure pI in the inner chamber 28 decreases until the spring 52 presses the third valve body 56 back into the third valve seat 62. This demonstrates a pressure-limiting function.

[0054] The function of the first valve body 38, which can be mechanically operated, in conjunction with the first valve seat 40 is described in detail in the published document DE 10 2014 209 278 A1. This function is used for pressure unloading during the preparation stage of operating the sleeve body 8, for releasing the plug chamber 14, or for decoupling the coupling plug, so that its disclosure is also referred to herein.

[0055] Figure 3 and 4The second and third embodiments are shown in the region of the third valve body which can be hydraulically actuated.

[0056] According to Figure 3 , unlike the first embodiment according to Figure 1 and 2 , the plate 158 is not closed, but is embodied with a coaxial through-hole 68. The third valve body 56, which is spherical, is centrally located at the edge of the through-hole distally of the valve seat 162. Upon the aforementioned disengagement of the third valve body 56 from the third valve seat 162, the third valve body 56 presses the plate 158 to the left in the Figure 3 , thereby forming the aforementioned pressure-limiting flow path. Here, as already described in the first embodiment, the pressure medium necessarily flows past the valve body 56 and, in addition, on the outer circumference, through the gap which is configured by the play between the plate 158 and the inner circumferential side 60 of the guide sleeve 48.

[0057] Figure 4 The third embodiment is shown with a third valve body 256 which can be hydraulically actuated, wherein the plate 258 is now embodied in one piece with the spherical valve body 256 and is arranged, for example, at the height of the equator thereof. Based on the oneness, no relative movement occurs any longer between the plate 258 with the guiding function and the valve body 256 with the sealing function. As already described in the two aforementioned embodiments, the pressure medium necessarily flows past the valve body 256 and, in addition, on the outer circumference, through the gap which is configured by the play between the plate 258 and the inner circumferential side 60 of the guide sleeve 48.

[0058] With the explained construction, the mechanically and hydraulically actuable load-unloading seat valve device 36 is physically divided into two coaxially arranged load-unloading seat valves: one, in particular mechanically actuable, for pressure unloading of the inner chamber 28, which has the first valve body 38 and the first valve seat 40, and one, hydraulically actuable, for limiting the pressure pi in the inner chamber 28, which has the third valve body 56; 256 and the third valve seat 62; 162; 262. Unlike in the solution according to the prior art, in both functions, pressure unloading upon mechanical actuation and pressure limitation by means of hydraulic actuation, are realized by the same valve body, so that the respective functions or the respective valve body and valve seat can be designed and manufactured separately from one another. This simplifies the design and manufacture.

[0059] The hydraulically actuable seat valve, together with its third valve body 56; 256, third valve seat 62; 262 and first spring 52, has the following features in terms of design and optimization.

[0060] The softer the first spring 52, the smaller the necessary opening pressure pI tolerance. It is therefore possible to forgo the adjustment possibility for the spring pretension of the first spring 52.

[0061] The smaller the diameter of the third valve body 56; 256, the smaller the necessary spring force of the first spring 52. However, a larger diameter of the third valve body 56; 256 is also possible in the case of a larger spring force.

[0062] The throttle bore 66 and the stepped bore 54; 154; 254, in particular the radially narrowing section thereof, lead to a small pressure-limiting flow due to the throttling effect, so that the third valve body 56; 256 better returns into the third valve seat 62; 262 after the opening stroke of the third valve body 56; 256.

[0063] A smaller seat angle of the third valve seat 62; 262 likewise leads to a better return of the third valve body 56; 256 into its third valve seat 62; 262.

[0064] An overflow channel which is configured, for example milled or getaumelt, in the third valve body 56; 256 on the circumference around the stepped bore 54; 154, in particular with a herringbone or other star-shaped cross section, enables an optimal guidance of the third valve body 56 in the stepped bore 54; 154.

[0065] The rounded outer peripheral edge of the plate 58; 158; 258 and / or the soft material there prevents the plate 58; 158; 258 from being hooked when it is guided in the guide sleeve 48.

[0066] A small play of the plate 58; 158; 258 in the guide sleeve 48 enables the avoidance of a tilted state on the third valve body 56; 256 and thus a transverse force. The third valve body then reliably enters its third valve seat 62; 262.

[0067] A hydraulic coupling sleeve for coupling with a hydraulic coupling plug is disclosed, which has a supply-seat valve device by means of which a supply flow path can be configured between a supply chamber of the coupling sleeve and a plug chamber by means of the actuation of the supply-seat valve device, and has a load-unload-seat valve device by means of which, on the one hand, a pressure unloading of an inner chamber of the coupling sleeve facing a pressure medium tank and, on the other hand, a pressure limitation in the inner chamber can be effected by means of the actuation of the load-unload-seat valve device. Here, the valve bodies with the associated valve seats are arranged coaxially with respect to one another separately from one another for the pressure unloading and the pressure limitation.

[0068] List of reference signs:

[0069] 1 coupling sleeve

[0070] 2 valve block

[0071] 4 coupling housing

[0072] 6 inner peripheral surface

[0073] 8 sleeve body

[0074] 10 center axis

[0075] 12 first component

[0076] 14 plug chamber

[0077] 16 second component

[0078] 18 through recess

[0079] 20 latch ball

[0080] 22 low pressure chamber

[0081] 24 supply chamber

[0082] 26 radial bore

[0083] 28 inner chamber

[0084] 30 second valve seat

[0085] 32 second valve body

[0086] 34 second spring

[0087] 36 load-unloading seat valve device

[0088] 38 first valve body

[0089] 40 first valve seat

[0090] 42 through recess

[0091] 44 sealing flange

[0092] 46 guide flange

[0093] 48 guide sleeve

[0094] 50 tank bottom

[0095] 52 first spring

[0096] 54 step / choke valve bore

[0097] 56; 256 third valve body

[0098] 58; 158; 258 plate

[0099] 60 inner peripheral surface

[0100] 62; 262 third valve seat

[0101] 64 cover sleeve

[0102] 66 throttle orifice

[0103] 68 through hole

[0104] pV pressure in supply chamber

[0105] pS pressure in plug chamber

[0106] pI pressure in inner chamber

[0107] pT pressure in low pressure chamber.

Claims

1. Hydraulic coupling sleeve for coupling with a hydraulic coupling plug, the coupling sleeve having a coupling housing (4) and a sleeve body (8) movable in the coupling housing and operable for closing or opening the coupling, the sleeve body having a plug chamber (14) for at least partially receiving the coupling plug and for fluidly connecting the coupling plug, a supply chamber (24) for fluidly connecting with an external supply channel, a low-pressure chamber (22) for fluidly connecting with a pressure medium tank, and an inner chamber (28) fluidly connected with the supply chamber (24), wherein The supply-seat valve device (30, 32) is provided, by manipulation of which a supply flow path can be configured between the supply chamber (24) and the plug chamber (14), and wherein a load-unloading seat valve device (36) is provided, by manipulation of which the inner chamber (28) towards the low-pressure chamber (22) can be pressure-unloaded and by further manipulation of which depending on the pressure (pl) in the inner chamber (28) the pressure (pl) in the inner chamber (28) can be limited, characterized in that the load-unloading seat valve device (36) has for the pressure-unloading an actuatable first valve body (38) with an associated valve seat (40) and for the pressure-limiting a further, according to the pressure (pl) actuatable third valve body (56; 256) with an associated valve seat (62; 262), which valve bodies are arranged coaxially.

2. The coupling sleeve of claim 1, wherein, The first valve body (38) and the third valve body (56; 256) of the load-unloading seat valve device (36) have oppositely arranged actuating directions.

3. The coupling sleeve of claim 1 or 2, wherein, The first valve body (38) and the third valve body (56; 256) of the load-unloading seat valve device (36) are coupled by a first spring (52) and are loaded in the respectively associated valve seat (40, 62; 40, 262). The valve seat (62; 262) of the second valve body (32) of the supply-seat valve device (32, 30) and the third valve body (56; 256) of the load-unloading seat valve device (36) are coupled by a second spring (34) and are loaded in their respective actuating directions oppositely towards a closed direction.

4. The coupling sleeve of claim 1 or 2, wherein, The first valve body (38) of the load-unloading seat valve device (36) and the second valve body (32) of the supply-seat valve device (32, 30) have oppositely arranged actuating directions.

5. The coupling sleeve of claim 1 or 2, wherein, 6. The coupling sleeve according to claim 1 or 2, having a guide sleeve (48) in which the first valve body (38) and the third valve body (56; 256) of the load-unloading seat valve device (36) are arranged and guided in series. The guide sleeve (48) is pot-shaped and the first valve body (38) of the load-unloading seat valve device (36) projects from a pot opening.

7. The coupling sleeve of claim 6, wherein, The guide sleeve (48) is pot-shaped and the valve seat (62; 262) of the further third valve body (56; 256) of the load-unloading seat valve device (36) according to the pressure (pl) in the inner chamber (28) is configured at a pot bottom (50) which is penetrated by a first throttle bore (54; 254) from the valve seat (62; 262) in the direction of the inner chamber (28).

8. The coupling sleeve of claim 6, wherein, ​ 9. The coupling sleeve of claim 1 or 2, wherein, The sealing section of the third valve body (56; 256) of the load-unloading seat valve device (36) which is actuated in accordance with the pressure (pl) in the inner chamber (28) and which has a valve seat (62; 262) associated therewith is a solid body or has at least one ball section or cone section.

10. The coupling sleeve of claim 9, wherein, The sealing section is a ball or a cone.

11. The coupling sleeve of claim 3, wherein, The diameter of the first spring (52) is greater than the diameter of the sealing section of the third valve body (56; 256) of the load-unloading seat valve device (36) which is actuated in accordance with the pressure (pl) in the inner chamber (28), wherein a support section (158; 258) is arranged separately from the sealing section, movably or connected to the sealing section or in one piece with the sealing section, at which the first spring (52) is supported.

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