Abstract:
A valve assembly, in particular a solenoid valve, is disclosed. The valve assembly includes an at least two-part housing that has a first housing sleeve and a second housing sleeve, the housing sleeves being held against each other by compression of a fastening zone. The valve assembly further includes a valve receptacle in which the valve is inserted and by means of which a press-in ring positioned in the region of the fastening zone is held. The press-in ring rests radially against the first housing sleeve and axially against the second housing sleeve.

Description:
This application is a 35 U.S.C. §371 National Stage Application of PCT/EP2010/066861, filed on Nov. 5, 2010, which claims the benefit of priority to Serial No. DE 10 2009 060 729.3, filed on Dec. 29, 2009 in Germany, the disclosures of which are incorporated herein by reference in their entirety. 
     The disclosure concerns a valve assembly with a valve, in particular a solenoid valve, which comprises an at least two-part housing that has a first housing sleeve and a second housing sleeve, wherein the housing sleeves are held against each other by compression of a fastening zone, and with a valve receptacle in which the valve is inserted and held by means of a press-in ring lying in the region of the fastening zone. 
     BACKGROUND 
     Valve assemblies of the generic type are known. They are used in particular for hydraulic monitoring and control purposes, for example in brake circuits of motor vehicles. Here the valve has an at least two-part housing wherein the housing parts are formed as housing sleeves and are pressed together in a fastening zone for connection. This design is commonly used, in particular in normally closed solenoid valves, for safe and economic production. Here the first housing sleeve has a stepped collar which is compressed radially by the outer wall of the second valve sleeve. The disadvantage is that when such valves are installed by pressing into a valve receptacle to create a valve assembly, force is transmitted via the stepped collar which extends over the second valve sleeve in the fastening zone. As a result in unfavorable cases, previously set valve key values and specifications can be achieved since, on unfavorable force transmission, plastic deformations can occur in the region of the stepped collar of the first valve sleeve. It is practically impossible to allow in advance for such possible deformations from force transmission on pressing the valve into the valve receptacle since the press-in force to be applied can vary substantially from valve to valve and can fluctuate within the range of several Kilonewtons. 
     SUMMARY 
     These drawbacks are advantageously avoided with the proposed valve assembly. A valve assembly is proposed with a valve, in particular with a solenoid valve, which comprises an at least two-part housing that has a first housing sleeve and a second housing sleeve, the housing sleeves being held against each other by compression of a fastening zone, and with a valve receptacle in which the valve is inserted and held by means of a press-in ring lying in the region of the fastening zone. Here it is proposed that the press-in ring lies radially against the first housing sleeve and axially against the second housing sleeve. The press-in ring consequently applies axial pressure on the second housing sleeve but (only) radial pressure on the first housing sleeve. The force transmission to the second housing sleeve consequently takes places not via the first housing sleeve but directly by the axial contact on the second housing sleeve. Material stress on the first housing sleeve, in particular an undesirable plastic deformation, in the contact region of the press-in ring or by force application through the press-in ring cannot therefore occur. The force to be applied to install the valve in the valve receptacle is applied directly to the second housing sleeve in the axial direction. 
     In a further embodiment it is provided that the second housing sleeve has an axial ring groove in which the first housing sleeve engages. The second housing sleeve has an axial ring groove formed in the axial direction and open in the direction of the press-in ring to be used to mount the valve assembly. The first housing sleeve engages in this axial ring groove. In contrast to the prior art, the second housing sleeve is consequently not surrounded on the outside by at least one segment of the first housing sleeve. The first housing sleeve is rather held by the axial ring groove with its open end region facing the second housing sleeve. 
     In a preferred embodiment the first housing sleeve engages with an outward pointing ring flange or with an outward turned crimp edge in the axial ring groove of the second housing sleeve. For this the first housing sleeve has the ring flange directed outward i.e. formed toward the outside in the radial direction, or the outward turned crimp edge, in the region of which there is to some extent a reversal of the material course direction in the backward direction of the first housing sleeve, and which viewed in cross section constitutes an approximately upwardly open eyelet. 
     Preferably the press-in ring axially pressurizes to the ring flange or the crimp edge. This further secures the first and second housing sleeve against axial separation. Also via the ring flange or particularly advantageously via the outward turned crimp edge compressed axially by the press-in ring, a seal of the first and second housing sleeve is achieved via the press-in ring. This seal acts in addition to the compression of the first and second housing sleeve in the fastening zone. In particular the crimp edge and/or the ring flange can be matched to the depth of the axial ring groove so that on contact of the press-in ring, the desired sealing effect is achieved, for example by an expansion of the crimp edge caused by axial pressurization via the press-in ring and filling the groove width of the axial ring groove. In particular very advantageously, the depth of the ring groove can be matched to the material thickness of the ring flange. 
     In a further embodiment it is proposed that the press-in ring lies on a face wall of the second housing sleeve, forming an axial stop, wherein the face wall stands at an angle, in particular a 90° angle, to a side wall of the axle ring groove and abuts the latter. The axial ring groove has a side wall which stands at an angle, in particular a 90° angle, to the face wall and abuts the latter, for example forming a side of the axial ring groove. This face wall forms the axial stop for the press-in ring. The press-in ring consequently transmits the force to this axial stop so that the force is transferred by the press-in ring to the second housing sleeve and there is no significant force application to the first housing sleeve or its ring flange or crimp edge, and undesirable effects on their material structure are therefore advantageously avoided. 
     In a further embodiment it is proposed that the press-in ring lies axially on a ring step of the valve receptacle. By lying on the ring step formed in or on the valve receptacle, a defined valve seat is achieved in the valve receptacle. The press-in ring is namely limited in its forward movement by the ring step when the valve is pressed in in the axial direction over the second housing sleeve. Excessive pressing in is thus advantageously avoided. 
     In a further embodiment it is proposed that the side walls of the axial ring groove are formed with different heights. The axial ring groove consequently, viewed in cross section, is not formed symmetrically but has side walls of different heights. 
     In one embodiment the inner side wall of the axial ring groove is formed higher than the outer side wall of the axial ring groove. 
     Furthermore it is proposed that the valve assembly belongs to an ABS, TCS and/or ESP system of a motor vehicle. Such valve assemblies can be used particularly advantageously and economically in particular in such hydraulic or electro-hydraulic systems, wherein due to the valve assembly described a very high level of reliability and operating safety is guaranteed with simplified production. 
     Further advantageous embodiments arise from the subclaims and combinations thereof. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Features of the disclosure are now explained in more detail below with reference to embodiment examples without being restricted to these in which examples: 
         FIG. 1  shows a valve with a first housing sleeve with an outward pointing ring flange, and 
         FIG. 2  shows a valve with an outward turned crimp edge. 
     
    
    
     DETAILED DESCRIPTION 
       FIG. 1  shows in segments, in longitudinal section view, a solenoid valve  1  with a two-part housing  2 , wherein the housing  2  is formed by a first housing sleeve  3  and a second housing sleeve  4  adjacent thereto in the axial direction. The solenoid valve  1  is here shown in its installation position in a pump housing  5  of a hydraulic unit of a motor vehicle. To hold the solenoid valve  1 , the pump housing  5  has a valve receptacle  6  which communicates with a hydraulic channel  7  and wherein the solenoid valve  1  is inserted in the valve receptacle  6  in axial direction R such that a supply opening  8  made on the face of the second housing sleeve  4  for the medium which communicates with a valve seat  9 , adjacent in the axial extent of the solenoid valve  1 , protrudes into the region of the hydraulic channel  7 . The solenoid valve  1  in the installation position shown is held on the pump housing  5  by a press-in ring  10  which axially pressurizes the solenoid valve  1  and rests on the second housing sleeve  4  of the solenoid valve in the axial direction and on the first housing half  3  of the solenoid valve  1  in the radial direction. The press-in ring  10  is further supported on an inner wall  11  of the valve receptacle  6  and in the axial direction on a valve receptacle ring step  12 . The first housing sleeve  3  on its end  13  facing the second housing half  4  has a peripheral ring flange  14  which lies in an axial ring groove  15  peripheral the second housing sleeve  4  and facing the first housing sleeve  3 . The axial ring groove  15  has a groove base  16  and side walls  17 , wherein an inner side wall  18  is higher than an outer side wall  19  of the axial ring groove  15 . The outer side wall  19  is limited radially outwardly at the top by a face wall  20 . The face wall  20  here stands at a right angle (90° angle) to the outer side wall  19 . The face wall  20  is pressurized in the axial direction by the press-in ring  10 , wherein the face wall  20  forms an axial stop  21 . The axial stop  21  here serves, when the solenoid valve  1  is pressed into the valve receptacle  6  by means of the press-in ring  10 , to transmit force to the solenoid valve  1  via the second housing sleeve  4 . The first housing sleeve  3  is here not pressurized or only to a slight extent (namely by unavoidable friction connection always present) by force in axial direction  30  R so that in the region of the connection of the first housing sleeve  3  and second housing sleeve  4 , namely in a fastening zone  22  in which the first housing sleeve  3  and the second housing sleeve  4  are held against each other for example by compression before installation in  35  the valve receptacle  6 , there is no undesirable force application; in the region of the fastening zone  22  there is merely a contact of the press-in ring  10  on the first housing sleeve in the radial direction. This avoids undesirable deformations or deterioration of the housing  2  in the region of the fastening zone  22  when pressed in by the press-in ring  10 , since substantial forces must be applied to the solenoid valve  1  for pressing into the valve receptacle  6  by means of the press-in ring  10 . In the present embodiment these forces are applied in axial direction R only by the axial stop  21  so that a reliable and constant force application is possible without deterioration in the fastening zone  22 . To guarantee this, the outer side wall  19  is formed so high that it either only projects slightly beyond a material thickness d of the first housing sleeve  3  in the region of the ring flange  14  so that the ring flange  14  itself which lies in the axial ring groove  15  is subject to no pressurization by force or only negligible pressurization by force in the axial direction R, or it is structured such that the ring flange  14  which lies in the axial ring groove  15  is subject to pressurization by force in axial direction R such that it is pressed tightly into the groove base  16 . In this way an additional peripheral seal of the first housing sleeve  3  on the second housing sleeve  4  is achieved in the regions of the groove base  16  and between ring flange  14  and press-in ring  10 . 
       FIG. 2  shows a solenoid valve  1  of substantially the same design as described in  FIG. 1 , in its installation position in the pump housing  5 . Consequently only the deviations of the structural design from the embodiment shown in  FIG. 1  are described. By contrast to the embodiment shown in  FIG. 1 , the first housing sleeve  3  does not have the ring flange  14  shown in  FIG. 1  but an outward turned crimp edge  23 . The crimp edge  23  lies in the axial ring groove  15  which lies on the periphery of the face of the second housing sleeve  4  and is limited by the groove base  16  and side walls  17 , wherein the side walls  17  stand at a right angle to the groove base  16  and the crimp edge  23  rests on the groove base  16  in axial direction R. The crimp edge  23  viewed in cross section here has the form of an outwardly curved eyelet  24  open at the top. The axial ring groove has an inner side wall  18  and an outer side wall  19 , wherein the outer side wall  19  in the longitudinal extent of the solenoid valve  1  is formed so high that it approximately reaches a height h of the crimp edge  23  or the crimp edge  23  projects out of the axial ring groove  15  slightly beyond the outer side wall  19 . The outer side wall  19  again abuts at a 90° angle the axial stop  21  which is formed by the face wall  20  and is pressurized by the press-in ring  10  in axial direction R and on installation in the valve receptacle  6  of the pump housing  5 , presses in the solenoid valve  1  and holds it in the installation position. If the crimp edge  23  protrudes slightly beyond the outer side wall  19 , its edge end  25  which protrudes beyond the outer side wall  19  in the direction towards the press-in ring  10 , is also pressurized by force such that the crimp edge  23  is deformed, pressing the crimp edge  23 —utilizing to the maximum the expansion of the axial ring groove  15 —against the groove base  16  and the side walls  17  of the axial ring groove  15 , and thus because of the geometry of the crimp edge  23 —namely forming an expanded eyelet  24  when viewed in cross section—causing it to lie with an all-round seal against the side walls  17  and the groove base  16 . Again on pressing the solenoid valve  1  into the valve receptacle  6  of the pump housing  5 , force is transmitted via the press-in ring  10  via the axial stop  21  formed on the second housing sleeve  4 , and not in the region of the fastening zone  22  in which the first housing sleeve  3  and second housing sleeve  4  are held against each other. Here again highly advantageously, a deformation of the housing  2  by force transmission on pressing in the solenoid valve  1 , which is possible in the prior art by a possible undesirable force transmission in the region of the fastening zone  22 , is avoided.