Patent Publication Number: US-10788057-B2

Title: Hydraulic valve body and hydraulic valve mechanism comprising the body

Description:
PRIORITY 
     This application is a continuation application of International application number PCT/FI2016/050419 filed on Jun. 13, 2016 and claiming priority of Finnish national applications number FI20155450 filed on Jun. 11, 2015 and FI20155938 filed on Dec. 12, 2015, the contents of both of which are incorporated herein by reference. 
    
    
     FIELD OF THE INVENTION 
     The invention relates to a hydraulic valve body, which is adapted to be used for controlling actuators external of the body. In addition, the invention relates to a hydraulic valve mechanism comprising said body. 
     BACKGROUND 
     The prior art discloses a variety of hydraulic valve bodies for controlling actuators external of the body. Hydraulic bodies are used, by controlling valves included therein, to guide a hydraulic fluid, such as hydraulic oil, in a desired manner to specific targets. Inlet fittings included in a hydraulic valve body have hydraulic lines connected thereto and, respectively, hose fittings have hydraulic hoses connected thereto. It is by controlling and moving spindles present inside the body that hydraulic oil is enabled to proceed to specific hoses. Such a control can be implemented by being managed electrically, pneumatically or mechanically. When using hydraulic oils, the hoses are occasionally subjected to pressure shocks, which may inflict damage. The occurrence of mishaps is averted by using safety valves as well as non-return valves. 
     One such hydraulic valve body is shown in  FIG. 1  (Prior Art), wherein the body comprises channels therein, hose fittings (C 1 -C 6 ) for connecting actuators (E 1 -E 4 ), and inlet fittings (P 1 , P 2 ) for hydraulic fluid. The body is further outfitted with sites for control elements, such as for externally controlled spindles, for guiding the fluid to a specific hose fitting. The body also comprises sites for one or more safety valves to be accommodated therein, whose cartridge chambers are connected with a channel to a return fitting for returning to a reservoir/pressure accumulator the hydraulic fluid coming in by way of the safety valve (the Applicant&#39;s valve body “E8312P4”). 
     A problem with many prior art solutions is nevertheless for example not as such enabling the execution of very many actions independent of each other. In addition, some valve mechanisms of the prior art do not make it possible that the pressure spike caused by a shock applied on an actuator or on its other side, for example on the cylinder piston side, be smoothly discharged onto the cylinder rod side or elsewhere, whereby the actuator or the valve mechanism or both may be wrecked by the pressure shock. 
     Moreover, the prior known solutions do not enable for example a floating actuator position, which is for example where the actuator is used to control a heavy machine&#39;s drawbars to which is linked a soil working plow. Plowing provides an optimal result with a so-called floating position, wherein the drawbars&#39; mechanical side guards are open. This causes problems whenever the plow is lifted up as it is free to swing uncontrollably in lateral direction. There are existing solutions, wherein the lateral adjustment of drawbars (at the same time, the side guards as well) is replaced by hydraulic cylinders (actuators). The current solutions do not, however, allow for a floating position, nor pressure shocks applied to drawbars and thereby to side guards. 
     SUMMARY OF THE INVENTION 
     One objective of the invention is to introduce such a hydraulic valve body which enables elimination or at least alleviation of the prior art-related problems. According to one embodiment, the invention endeavors to provide such a single hydraulic valve body that has no need for hose installations between various valves. Another objective is to simplify the installation of valves as well as components related thereto, as well as to introduce such a hydraulic valve body which is simple in construction and which single valve body is configurable in view of attaining at least the foregoing (and to be described more precisely elsewhere in this document) functions (most preferably at least 11 different flow circuits and functions). It is one objective of the invention to introduce such a hydraulic valve body which is adaptable for controlling several types of actuators, yet with the number of body components, such as valves, as few as possible. 
     Such objectives of the invention are attained with a hydraulic valve body according to claim  1 . 
     The hydraulic valve body of the invention is characterized by what is presented in claim  1  directed to a hydraulic valve body. In addition, the hydraulic valve mechanism of the invention is characterized by what is presented in claim  15  directed to a hydraulic valve mechanism. 
     In the invention, according to a first embodiment, the hydraulic valve body comprises two main lines for bringing pressurized hydraulic fluid into a channel system of said body and further out of the channel system. The main fittings are most preferably adapted to be coupled with the pressure and return lines of a heavy machine. The body comprises at least two outlet fittings for conducting hydraulic fluid from the body&#39;s channel system to actuators and two respective inlet fittings for conducting hydraulic fluid from the actuators back into the body&#39;s channel system. 
     The body further comprises a first channel provided between the first main line and the first outlet and a second channel provided between the first main line and the second outlet, as well as a third channel provided between the second main line and the first inlet. In addition, between the first inlet and the second inlet the body is provided with a third connecting channel. 
     According to this embodiment, in connection with two of said outlet fittings, the body is further provided with first and second cartridge chambers for two control elements operating independently of each other for conducting a pressure flow by way of the respective first or second channel from the first main line to at least one actuator connected to the outlets. 
     In connection with one of said inlet fittings, the body is further provided with a third cartridge chamber for a third control element operating independently of the other control elements actuators for conducting a pressure flow from the actuator connected to at least one of the inlet fittings back into the second main line by way of the third channel, or by way of the third connecting channel and the third channel. 
     According to one example, the control element can be for example a solenoid valve. According to one example, said control channels are boreholes which can be fitted with a control element, for example a solenoid valve. 
     In the invention, according to one embodiment, the hydraulic valve mechanism comprises a body as described in the foregoing. The mechanism further comprises first and second cartridge chambers provided in connection with two of said outlet fittings, as well as first and second control elements, for example solenoid valves, provided in said first and second control channels and capable of being controlled from outside independently of each other, for conducting a pressure flow from the first main line by way of the first or second channel in a controllable manner to at least one actuator connected to the outlet fittings. Still further, the mechanism comprises a third cartridge chamber provided in connection with one of said inlet fittings and therein a third control element operating independently of the other control elements for conducting a pressure flow from an actuator connected to at least one of the inlet fittings back into the second main line in a controllable manner by way of the third channel, or by way of the third connecting channel and the third channel. 
     According to one example, the control element may comprise a movable spindle provided in the cartridge chamber (for example a seat spindle or the like spindle or other tool known for a person skilled in the art), said spindle being adapted to achieve at least some of the configurations and functions (flow circuits) of said body&#39;s channel system. Said control element can be for example a solenoid valve or a pneumatically, hydraulically or mechanically controlled valve. 
     According to one embodiment of the invention, the valve body can be expanded with attachments, such that the coupling and controlling of even several hydraulically controlled implements is possible with a mechanism of the invention. 
     The invention offers distinct benefits with respect to the prior art. Now, a single valve body, which includes channel structures described in this document, is capable of achieving the aforesaid functions, as well as other further functions described in this document, at least 11 functions in total. It is particularly notable that the valve body solution of the invention, its channel systems, and connections between various outlets and inlets as well as the main lines, are adapted in such a way that all said functions are achievable by using just three external control elements such as solenoid valves. This is a clear advantage because, for example in prior known solutions, the control of two actuators connected to the body&#39;s two outlets and inlets has required four control elements and, in addition, said body solutions have not enabled as many different functions as the body of the present invention, such as for example a floating position and a viable control of pressure shocks. Accordingly, the execution of said functions no longer necessitates several separate valve bodies and at least four or more external control elements such as solenoid valves. This is an obvious cost saving and moreover the valve body and its operation is considerably more reliable with moving and controlled parts fewer than before. 
     It should further be noted that the mechanism of the invention can be used for example for hydraulically controlling, particularly for example in lateral direction, the side guards of a tractor or other heavy machine, and it can be either an attachment for machines already in existence or a component capable of being integrated with new machines as early as in the process of manufacturing the machines. Indeed, by means of a hydraulic mechanism of the invention, it is possible to hydraulically control for example the side guards of currently available tractors, especially in lateral direction, independently of each other. Likewise, in up/down direction, the control is possible as the body has two sets of additional outlets and inlets. This facilitates, first of all, the hitching of work implements to a tractor, but is also a factor contributing qualitatively to the actual work performance. The mechanism for example enables the free floating position of a tractor-hitched work implement, which is very important for example in the process of drawing a furrow in a plowing position, whereby the management of lateral forces has a very important role (the pressure generated by lateral forces can be discharged from side to side by means of a mechanism of the invention by opening the valves between sidebars in the mechanism). In addition, and at the same time, the invention makes it possible to limit the lateral movement of a tractor-hitched work implement as the work implement is in an uplifted position, which is a significant safety factor, denying (locking) a lateral movement of the work implement for example for the duration of transport (by closing the valves between sidebars in the mechanism). 
    
    
     
       SHORT DESCRIPTION OF THE FIGURES 
       In the next section, preferred embodiments of the invention will be discussed slightly more precisely with reference to the accompanying figures, in which 
         FIG. 1  shows one valve body according to the prior art, 
         FIG. 2  shows one exemplary valve body and flow circuit according to one preferred embodiment of the invention, 
         FIG. 3  shows one exemplary valve body and six different flow circuits according to one preferred embodiment of the invention, 
         FIG. 4  shows one exemplary valve body and four different flow circuits according to one preferred embodiment of the invention, 
         FIG. 5  shows one exemplary valve body and one twelfth flow circuit according to one preferred embodiment of the invention, 
         FIG. 6  shows one exemplary hydraulic mechanism comprising a valve body, according to one preferred embodiment of the invention, in a view from above, and 
         FIG. 7  shows one exemplary hydraulic mechanism comprising a valve body, according to one preferred embodiment of the invention, in a view from below. 
     
    
    
     DETAILED DESCRIPTION OF THE INVENTION 
       FIG. 1  has been described in the prior art section. 
       FIGS. 2-5  illustrate exemplary hydraulic valve bodies  100  and flow circuits according to certain preferred embodiments of the invention. 
     The hydraulic valve body  100  comprises two main lines P 1 , P 2  for bringing pressurized hydraulic fluid into said body&#39;s channel system and further out of the channel system. The body comprises at least first and second outlet fittings C 1 , D 1  for conducting hydraulic fluid from the body&#39;s channel system to actuators E 1 , E 2 , such as cylinders, for example to cylinders used for laterally controlling the drawbars of a heavy machine such as a tractor. The body further comprises respective first and second inlet fittings C 2 , D 2  for conducting hydraulic fluid from the actuators E 1 , E 2  back into the body&#39;s channel system and into the second main line functioning as a return channel. 
     The body comprises also a first channel K 1  provided between the first main line P 1  and the first outlet C 1 , a second channel K 2  provided between the first main line P 1  and the second outlet D 1 , and a third channel K 3  provided between the second main line P 2  and the first inlet C 2 . In addition, the body comprises a third connecting channel YK 3  provided between the first inlet C 2  and the second inlet D 2 . The channels and lines are preferably holes drilled in the body structure. 
     In connection with the first and second outlet fittings C 1 , D 1  are provided first and second cartridge chambers MK 1 , MK 2  for two control elements M 1 , M 2 , such as solenoid valves, operating independently of each other. 
     The control elements M 1 , M 2  are used most preferably for conducting a pressure flow from the first main line P 1  by way of the first or the second channel K 1 , K 2  to at least one actuator E 1 , E 2  connected to the first or the second inlet fitting C 1 , D 1 . 
     In addition, according to one embodiment, in connection with the first inlet fitting C 2  is provided a third cartridge chamber MK 3  for a third control element M 3  working independently of the other control elements. It should be noted that, by virtue of a body structure of the invention, said third control element can be used for conducting a pressure flow in a controlled manner from the actuator E 1 , E 2  connected either to the first and/or the second inlet fitting C 2 , D 2  back into the second main line P 2  by way of the third channel K 3 , or by way of the third connecting channel YK 3  and the third channel K 3 . It is particularly notable that, by virtue of a configuration of the invention, in connection with the second inlet there is no need for a dedicated separate control element or a control channel for the same, because the pressure flow can be conducted to the third control element M 3  by way of the third connecting channel YK 3 . 
     The control channels are most preferably holes, which are drilled in the body structure and can be fitted with control elements, such as solenoid valves, in a valve mechanism comprising the body structure. In the machining process, the holes are most preferably drilled from one of the facets of the body, possibly necessitating the plugging of boreholes unless the discussed hole is fitted with some element, such as an actuator, a safety valve, a control element, or something else. 
     According to one embodiment of the invention, between the first outlet C 1  and the second outlet D 1  the body is provided with a second connecting channel YK 2 . Moreover, in connection with the first outlet fitting C 1 , the body is provided with a first control channel MV 1  for coupling a first pressure safety/non-return valve V 1  and for controlling a pressure flow between the outlet C 1  and the connecting channel YK 2  and/or YK 1 . Also, in connection with the second outlet fitting D 1  is provided a second control channel M 2  for coupling a second pressure safety/non-return valve V 2  for controlling a pressure flow between the outlet C 2  and the connecting channel YK 2  and/or YK 1 . 
     According to one embodiment, in connection with the first inlet fitting C 2 , the body is also provided with a third control channel MV 3  for coupling a third pressure safety/non-return valve V 3  and for controlling a pressure flow between the inlet C 2  and the first connecting channel YK 1 . 
     In addition, according to one embodiment of the invention, in connection with the second inlet D 2  is provided a fourth control channel M 4  for coupling a fourth pressure safety/non-return valve V 4  and for controlling a pressure flow between the second inlet D 2  and the first external fitting PK 1 . According to one example, said first external fitting PK 1  is provided in connection with the second inlet D 2  and is adapted to be coupled with a (preferably external) pressure accumulator or tank, into which the overpressure of a given magnitude is able to discharge by way of the fourth pressure safety/non-return valve V 4  and from which pressure accumulator, if necessary, is allowed respectively a pressure flow by way of the fourth pressure safety/non-return valve V 4  into the third connecting channel YK 3  and further, as described elsewhere in this document, to actuators as required by the situation. 
     Still furthermore, according to one embodiment of the invention, the body is provided between the second main line P 2  and the second outlet D 1  with a fifth channel K 5 . In addition, in connection with the second main line P 2  is provided at least one fifth cartridge chamber MK 5  for at least one fifth control element M 5  working independently of the other control elements. Said fifth cartridge chamber MK 5  extends into the fifth channel K 5  and thereby makes possible a twelfth flow circuit from the second outlet D 1  along the fifth channel K 5  to the second main line P 2 . 
     According to one example, the first, second and third control channels MV 1 , MV 2 , MV 3 , or a portion included therein, are vertical channels and the connecting channels YK 1  and YK 2  can be at lower level than for example the main lines P 1 , P 2  or the channels K 1 -K 3 . Further, according to one embodiment, the second inlet D 2 , or a portion included therein, is also a vertical channel. 
     First Flow Circuit (VP 1 ) for Enabling a First Function (E 1 , Operation of the Left-Hand Cylinder) ( FIG. 3 ) 
     According to one example, the first flow circuit VP 1  for enabling a first function comprises a first outlet C 1  and a first inlet C 2 . The first outlet C 1  is adapted to be connected onto a first side S 1  (piston side) of the first actuator E 1  for conducting a pressure flow from the first main line P 1  by way of a first channel K 1  onto the first side S 1  of the first actuator E 1 . The first inlet C 2 , on the other hand, is adapted to be connected onto a second side S 2  (left-hand side) of the same first actuator E 1  for conducting a pressure flow by way of a third channel K 3  to the second main line P 2 . 
     In operation (operation of the left-hand cylinder E 1 ), the control elements M 1  and M 3  of a hydraulic mechanism ( FIG. 5 ) are opened, whereby M 1  opens a line from the main line P 1  to the outlet C 1  and M 3  opens a line from the inlet C 2  to the main line (return) P 2 . 
     Second Flow Circuit (VP 2 ) for Enabling a Second Function (E 2 , Operation of the Right-Hand Cylinder) ( FIG. 3 ) 
     According to one example, the second flow circuit VP 2  for enabling a second function comprises a second outlet D 1  and a second inlet D 2 . The second outlet D 1  is adapted to be connected onto a first side S 3  (piston side) of the second actuator E 2  for conducting a pressure flow from the first main line P 1  by way of a second channel K 2  onto the first side S 3  of the second actuator E 2 . The second inlet D 2  is adapted to be connected onto a second side S 4  (rod side) of the second actuator E 2  for conducting a pressure flow by way of a third connecting channel YK 3  and a third channel K 3  into the second main line P 2 . 
     In operation (operation of the right-hand cylinder E 2 ), the control elements M 2  and M 3  of a hydraulic mechanism ( FIG. 5 ) are opened, whereby M 2  opens a line from the main line P 1  to the outlet D 1  and M 3  opens a line from C 2  to the main line (return) P 2 , the pressure flow being thus able to flow from the inlet D 2  by way of the connecting channel YK 3  to the main line (return) P 2 . 
     Third Flow Circuit (VP 3 ) for Enabling a Third Function (Floating Position) ( FIG. 2 ) 
     According to one example, the third flow circuit VP 3  for enabling a third function (for example the “floating position” of a soil working plough) comprises both first, second and third channels K 1 , K 2 , K 3 , a third connecting channel YK 3 , as well as first and second outlets C 1 , D 1  and first and second inlets C 2 , D 2 . The outlets and inlets are adapted to be connected (at least partially integral with each other in functional sense) to the first and the second actuators E 1 , E 2 . 
     In the third flow circuit configuration, the pressure applied onto the first sides S 1 , S 3  of the first and second actuators E 1 , E 2  is adapted to shift freely by way of the first and second outlets C 1 , D 1 , as well as by way of the first and second channels K 1 , K 2  connecting the same, and by way of the first main channel P 1 , from side to side (C 1 ↔D 1 ). In addition, the pressure applied onto the second sides S 2 , S 4  of the first and second actuators E 1 , E 2  is adapted to shift freely by way of the first and second inlets C 2 , D 2 , as well as by way of the third connecting channel YK 3  connecting the same, from side to side (C 2 ↔D 2 ). 
     In operation (operation of both cylinders E 1 , E 2 , “floating position”), the control elements M 1  and M 2  of a hydraulic mechanism ( FIG. 5 ) are opened, whereby M 1  opens a line from the main line P 1  to the outlet C 1  and M 2  opens a line from the main line P 1  to the outlet D 1 , the pressure flow being allowed to flow freely between the outlets C 1  and D 1  by way of the main line P 1  (the line from the piston side of E 1  to the piston side of E 2  is open). Likewise, the operation involves opening the hydraulic mechanism control element M 3 , whereby M 3  opens a line between the inlets C 2  and D 2  by way of the connecting channel YK 3  (the line from the rod side of E 1  to the rod side of E 2  is open). 
     Fourth Flow Circuit (VP 4 ) for Enabling a Fourth Function (Pressure Equalization of the Piston Side of E 1  onto the Rod Side of E 1 ) ( FIG. 3 ) 
     According to one example, the fourth flow circuit VP 4  for enabling a fourth function comprises a first outlet C 1  and a first inlet C 2 , as well as a first connecting channel K 1  provided therebetween, as well as between the first connecting channel YK 1  and the first outlet C 1  a first control channel MV 1  and therein a first pressure safety/non-return valve V 1 . The first outlet C 1  is adapted to be connected onto a first side S 1  (piston side) of the first actuator E 1  for conducting an overpressure generated on the first side of the actuator E 1  along the first connecting channel YK 1  to the first inlet C 2 . The first inlet C 2  is adapted to be connected onto a second side S 2  of the first actuator E 1  and thereby to primarily enable the overpressure conducted along the first connecting channel YK 1  to be equalized onto the second side S 2  (rod side) of the first actuator E 1 . 
     In operation, the overpressure is required to exceed a pressure value (for example 160 bar) of the first pressure safety/non-return valve V 1  and to advance over a third non-return valve V 3  to the first inlet. In operation, the control elements are closed. 
     Fifth Flow Circuit VP 5  for Enabling a Fifth Function (Pressure Equalization of the Piston Side of E 1  into an External Channel PK 1  and into a Pressure Accumulator or Tank Possibly Integrated Therewith) ( FIG. 3 ) 
     The fifth flow circuit VP 5  for enabling a fifth function comprises a first outlet C 1  and a first inlet C 2 , as well as a first connecting channel YK 1  provided therebetween, as well as between the first connecting channel YK 1  and the first outlet C 1  a first control channel MV 1  and therein a first pressure safety/non-return valve V 1 . It further comprises a third control channel MV 3  provided in connection with the first inlet fitting C 2  for coupling a third pressure safety/non-return valve V 3  and for conducting a pressure flow from the first connecting channel YK 1  to the first inlet C 2  and further into a third connecting channel YK 3  provided between the first and the second inlets C 2 , D 2 . 
     In addition, the fifth flow circuit VP 5  comprises a first external channel PK 1 , which is provided in connection with the third connecting channel YK 3  and/or the second inlet D 2  and which is adapted to be connected for example to a pressure accumulator or tank. In addition, the first outlet C 1  is adapted to be connected onto a first side S 1  (piston side) of the first actuator E 1  for conducting an overpressure generated on the first side of the actuator E 1  along the first connecting channel YK 1  and the third connecting channel YK 3  by way of the third pressure safety/non-return valve V 3  to the first inlet C 2  and further by way of the third connecting channel YK 3  to the second inlet D 2  and, by way of a fourth connecting channel YK 4  provided in connection therewith and by way of a fourth pressure safety/non-return valve V 4 , into the first external channel PK 1 . 
     In operation, the overpressure must exceed a pressure value (for example 160 bar) of the first pressure safety/non-return valve V 1  and a pressure value (for example 175 bar) of the fourth pressure safety/non-return valve V 4 . If the first external channel PK 1  is connected to a pressure accumulator, the pressure accumulator may have a threshold pressure for example of 150 bar. In operation, the valves are closed. 
     Sixth Flow Circuit VP 6  for Enabling a Sixth Function (Equalization of the Piston Side Underpressure of E 1  from the Rod Side) ( FIG. 3 ) 
     The sixth flow circuit VP 6  for enabling a sixth function comprises a first outlet C 1  and a first inlet C 2 , as well as a first connecting channel YK 1  which is connected at its first end to the first outlet C 1  by way of a first control channel MV 1  and a first pressure safety/non-return valve V 1  and at its second end connected to the first inlet C 2  by way of a third control channel MV 3  and a third pressure safety/non-return valve V 3 . 
     The first outlet C 1  is adapted to be connected onto a first side S 1  (piston side) of the first actuator E 1  and the first inlet C 2  is adapted to be connected onto a second side S 2  (rod side) of the first actuator E 1 . 
     In order to enable the equalization of an underpressure generated on the first side S 1  of the first actuator E 1 , the first outlet C 1  is adapted to conduct a pressure flow from the second side S 2  of the first actuator E 1  by way of the first inlet C 2  into the third control channel MV 3  and over the third pressure safety/non-return valve V 3  and further along the first connecting channel YK 1  into the first control channel MV 1  and over the first pressure safety/non-return valve V 1  and further by way of the first outlet C 1  onto the first side S 1  of the first actuator E 1 . 
     In operation, the pressure flow is required to exceed a pressure value (for example 130 bar) of the third pressure safety/non-return valve V 3 . In operation, the valves are closed. 
     Seventh Flow Circuit VP 7  for Enabling a Seventh Function (Equalization of the Piston Side Underpressure of E 1  from an External Channel PK 1  and Especially from a Pressure Accumulator Integrated Therewith) ( FIG. 3 ) 
     The seventh flow circuit VP 7  for enabling a seventh function comprises a first outlet C 1  and a first external channel PK 1 , as well as a first connecting channel YK 1  which is at its first end connected to the first outlet C 1  by way of a first control channel MV 1  and a first pressure safety/non-return valve V 1  and at its second end connected to the first inlet C 2  by way of a third control channel MV 3  and a third pressure safety/non-return valve V 3 , as well as a third connecting channel YK 3  provided between the first inlet C 2  and the second inlet D 2  and a fourth control channel MV 4  provided between the second inlet D 2  and the first external channel PK 1  and by way of a fourth pressure safety/non-return valve V 4 . 
     The first outlet C 1  is adapted to be connected onto a first side S 1  (piston side) of the first actuator E 1 . 
     In order to enable the equalization of an underpressure generated on the first side S 1  of the first actuator E 1 , the first outlet C 1  is adapted to conduct a pressure flow from the first external channel PK 1  along the fourth control channel MV 4  to the first outlet C 1  by way of the fourth pressure safety/non-return valve V 4 , the first inlet C 2 , the third connecting channel YK 3 , the second inlet D 2 , the third control channel MV 3 , the third pressure safety/non-return valve V 3 , and further by way of the first connecting channel YK 1  and the first pressure safety/non-return valve V 1 . 
     In operation, the pressure flow must exceed a pressure value (for example 130 bar) of the third pressure safety/non-return valve V 3 . In operation, the valves are closed. 
     Eighth Flow Circuit VP 8  for Enabling a Eighth Function (Equalization of the Piston Pressure of E 2  onto the Rod Side) ( FIG. 4 ) 
     In the eighth flow circuit configuration, the body comprises a second outlet D 1  and a first inlet C 2 , as well as a first connecting channel YK 1  provided therebetween and a second connecting channel YK 2  provided between the second outlet D 1  and the first connecting channel YK 1 . The second outlet D 1  connects with the second connecting channel YK 2  by way of a second control channel MV 2  and a second pressure safety/non-return valve V 2 . The first connecting channel YK 1  connects with the first inlet C 2  by way of a third control channel MV 3  and a third pressure safety/non-return valve V 3 . The configuration comprises a second inlet D 2  which connects with the first inlet C 2  by way of a third connecting channel YK 3 . 
     The eighth flow circuit VP 8  comprises the second outlet D 1  and the second inlet D 2 , and wherein the second outlet D 1  is adapted to be connected onto a first side S 3  (piston side) of the second actuator E 2  for conducting an overpressure generated on the first side of the actuator E 2  over the second control channel MV 2  and the second pressure safety/non-return valve V 2  and along the second connecting channel YK 2  into the first connecting channel YK 1  and further by way of the third control channel MV 3  and the third pressure safety/non-return valve V 3  to the first inlet C 2  and along the third connecting channel YK 3  to the second inlet D 2 , said second inlet D 2  being adapted to be connected onto a second side S 4  (rod side) of the second actuator E 2  and to primarily enable thereby the overpressure generated on the first side S 3  of the second actuator E 2  to be equalized onto the second side S 4  of the second actuator E 2 . 
     In operation, the overpressure must exceed a pressure value (for example 160 bar) of the second pressure safety/non-return valve V 2 . In operation, the valves are closed. 
     Ninth Flow Circuit VP 9  for Enabling a Ninth Function (Equalization of the Piston Overpressure of E 2  into an External Channel PK 1  or a Pressure Accumulator) ( FIG. 4 ) 
     In the ninth flow circuit configuration, the body comprises a second outlet D 1  and a first inlet C 2 , as well as a first connecting channel YK 1  provided therebetween and a second connecting channel YK 2  provided between the second outlet D 1  and the first connecting channel YK 1 . The second outlet D 1  connects with the second connecting channel YK 2  by way of a second control channel MV 2  and a second pressure safety/non-return valve V 2  and the first connecting channel YK 1  connects with the first inlet C 2  by way of a third control channel MV 3  and a third pressure safety/non-return valve V 3 . The configuration comprises also a second inlet D 2  connecting with the first inlet C 2  by way of a third connecting channel YK 3 , as well as a first external channel PK 1  connecting with the second inlet D 2  by way of a fourth control channel MV 4  and a fourth pressure safety/non-return valve V 4 . 
     The ninth flow circuit comprises the second outlet D 1  and the first external channel PK 1 , wherein the second outlet D 1  is adapted to be connected onto a first side S 3  (piston side) of the second actuator E 2  for conducting an overpressure generated on the first side of the actuator E 2  over the second control channel MV 2  and the second pressure safety/non-return valve V 2  and along the second connecting channel YK 2  into the first connecting channel YK 1  and further by way of the third control channel MV 3  and the third pressure safety/non-return valve V 3  to the first inlet C 2  and along the third connecting channel YK 3  to the second inlet D 2  and further into the first external channel PK 1  by way of the fourth control channel MV 4  and the fourth pressure safety/non-return valve V 4 . 
     In operation, the overpressure is required to exceed a pressure value (for example 160 bar) of the second pressure safety/non-return valve V 2  and a pressure value (for example 175 bar) of the fourth pressure safety/non-return valve V 4 . If the first external channel PK 1  is connected to a pressure accumulator, the pressure accumulator may have a threshold pressure for example of 150 bar. In operation, the valves are closed. 
     Tenth Flow Circuit VP 10  for Enabling a Tenth Function (Equalization of the Piston Side Underpressure of E 2  onto the Rod Side) ( FIG. 4 ) 
     The tenth flow circuit VP 10  comprises a second outlet D 1  and a first inlet C 2 , as well as a first connecting channel YK 1  provided therebetween and a second connecting channel YK 2  provided between the second outlet D 1  and the first connecting channel YK 1 , wherein the second outlet D 1  connects with the second connecting channel YK 2  by way of a second control channel MV 2  and a second pressure safety/non-return valve V 2  and wherein the first connecting channel YK 1  connects with the first inlet C 2  by way of a third control channel MV 3  and a third pressure safety/non-return valve V 3 . In addition, the flow circuit comprises a second inlet D 2  connecting with the first inlet C 2  by way of a third connecting channel YK 3 . 
     The second outlet D 1  is adapted to be connected onto a first side S 3  (piston side) of the second actuator E 2  and the second inlet D 2  is adapted to be connected onto a second side S 4  (rod side) of the second actuator E 2 . In order to enable the equalization of an underpressure generated on the first side S 3  of the second actuator E 2 , the second outlet D 1  is adapted to conduct a pressure flow from the second side S 4  of the second actuator E 2  by way of the second inlet D 2  along the third connecting channel YK 3  to the first inlet C 2  and over the third connecting channel YK 3  and the third pressure safety/non-return valve V 3  and further along the first connecting channel YK 1  into the second connecting channel YK 2  and further onto the first side S 3  of the second actuator E 2  over the second control channel MV 2  and the second pressure safety/non-return valve V 2  and further by way of the second outlet C 2 . 
     In operation, the overpressure is required to exceed a pressure value (for example 130 bar) of the third pressure safety/non-return valve V 3 . In operation, the valves are closed. 
     Eleventh Flow Circuit VP 11  for Enabling an Eleventh Function (Equalization of the Piston Side Underpressure of E 2  from an External Channel PK 1  and Especially from a Pressure Accumulator Integrated Therewith) ( FIG. 4 ) 
     The eleventh flow circuit VP 11  comprises a second outlet D 1  and a first external channel PK 1 , as well as a first connecting channel YK 1  provided between the second outlet D 1  and the first inlet C 2  and a second connecting channel YK 2  provided between the second outlet D 1  and the first connecting channel YK 1 . The second outlet D 1  connects with the second connecting channel YK 2  by way of a second control channel MV 2  and a second pressure safety/non-return valve V 2 , and the first connecting channel YK 1  connects with the first inlet C 2  by way of a third control channel MV 3  and a third pressure safety/non-return valve V 3 , as well as a second inlet D 2  which connects with the first inlet C 2  by way of a third connecting channel YK 3 , and moreover a fourth control channel MV 4  provided between the second inlet D 2  and the first external channel PK 1 , and a fourth pressure safety/non-return valve V 4 . 
     The second outlet D 1  is adapted to be connected onto a first side S 3  (piston side) of the second actuator E 2 . In order to enable the equalization of an underpressure generated on the first side S 3  of the second actuator E 2 , the second outlet D 1  is adapted to conduct a pressure flow from the first external channel PK 1  to the second outlet D 1  over the fourth control channel MV 4  and the fourth pressure safety/non-return valve V 4  and by way of the second inlet D 2  into the third connecting channel YK 3  and by way of the first inlet C 2  and the third control channel MV 3  and the third pressure safety/non-return valve V 3  further into the first connecting channel YK 1 , into the second connecting channel YK 2 , and further to the second outlet D 1  by way of the second control channel MV 2  and the second pressure safety/non-return valve V 2 . 
     In operation, the pressure flow is required to exceed a pressure value (for example 130 bar) of the third pressure safety/non-return valve V 3 . In operation, the valves are closed. 
     Twelfth Flow Circuit (VP 12 ) for Enabling a Twelfth Function (a Reverse Function of Actuators E 1  and E 2 , i.e. for Example a Function in which the Actuator&#39;s E 1  First Side or Piston Goes in and the Actuator&#39;s E 2  First Side or Piston Comes Out) ( FIG. 5 ) 
     The twelfth flow circuit VP 12  for enabling a twelfth function comprises first and second outlets C 1 , D 1  and first and second inlets C 2 , D 2 , as well as both a third connecting channel YK 3  provided between the first and second inlets C 2 , D 2  and a fifth channel K 5  provided between the second outlet D 1  and the second main line P 2 . The second outlet D 1  connects with the fifth channel K 5  and further with the second main line P 2  by way of a fifth cartridge chamber MK 5  and a fifth control element M 5  to be fitted thereto. 
     In the twelfth flow circuit, in order to enable the twelfth function, the first outlet C 1  is adapted to be connected onto a first side S 1  of the first actuator E 1  for conducting a pressure flow from the first main line P 1  by way of a first channel K 1  onto the first side S 1  (piston side) of the first actuator E 1 . In addition, the first inlet C 2  is adapted to be connected onto a second side S 2  (rod side) of the first actuator E 1  for conducting a pressure flow by way of a third connecting channel YK 3  to the second inlet fitting D 2 . The second inlet fitting D 2  is adapted in the twelfth flow circuit VP 12  to be connected onto a second side S 4  (rod side) of the second actuator E 2  for conducting a pressure flow from the inlet fitting D 2  onto the second side S 4  of the second actuator E 2 . In addition, the second outlet D 1  is adapted to be connected onto a first side (piston side) of the second actuator E 2  and further for conducting a pressure flow from the first side S 3  of the second actuator E 2  into the fifth channel K 5  associated with the first outlet D 1 . Said fifth channel K 5  is adapted to conduct said pressure flow into the second main line P 2 . 
     The operation (concurrent operation of cylinders E 1 , E 2 ) involves the opening of control elements M 1  and M 5  in a hydraulic mechanism ( FIG. 5 ), whereby M 1  opens a line from the main line P 1  to the outlet C 1 , and M 5  opens a line from the inlet D 1  to the main line (return) P 2 . In an exemplary operation, the cylinders can be coupled for example with the drawbars of a heavy machine, wherein, by controlling the control elements M 1  and M 2 , the drawbars can be concurrently moved either left or right (depending on whether the flow pressure is introduced into the main line P 1  as in the present case, or into the main line P 2  with the flow in a reverse direction, which is also possible). 
     According to one preferred embodiment of the invention, the hydraulic valve body further comprises at least third, most preferably also fourth outlets (B 1 , A 1 ) and respective inlets (B 2 , A 2 ). The body also comprises channels (KB 1 , KB 2 , KA 1 , KA 2 ) provided in the body between the first main line (P 1 ) and the outlets (B 1 , A 1 ) as well as between the second main line (P 2 ) and the inlets (B 2 , A 2 ), as well as cartridge chambers (MB 1 , MB 2 , MA 1 , MA 2 ) fitted in connection therewith for control elements (MAM 1 , MAM 2 , MBM 1 , MBM 2 ) operating independently of each other for conducting a pressure flow from the first main line (P 1 ) to at least one outlet fitting (B 1 , A 1 ) by way of either channel (KB 1 , KA 1 ) and for conducting a pressure flow into the second main line (P 2 ) from at least one inlet fitting (B 2 , A 2 ) by way of the channel (KB 2 , KA 2 ). 
     According to one preferred embodiment of the invention, the hydraulic valve body is adapted to be coupled with an additional body module  101  ( FIG. 5 ), wherein the additional body module comprises at least one additional outlet (X 1 , Y 1 ) and at least one respective additional inlet (X 2 , Y 2 ), as well as respective channels (KX 1 , KY 1 , KX 2 , KY 2 , not shown in the figures) between the main lines and the outlets and inlets, as well as respective cartridge chambers (not shown in the figures) for control elements MX 1 , MX 2 , MY 1 , MY 2 . 
       FIG. 5  shows one exemplary hydraulic mechanism  200  comprising the valve body  100  in accordance with one preferred embodiment of the invention, in a view from above, and  FIG. 6  one exemplary hydraulic mechanism  200  comprising the valve body  100 , in a view from below. 
     The control element is most preferably a seat type solenoid valve, which also functions at the same time as a lock and is practically leak-proof. 
     The above description has only presented a few embodiments for a solution of the invention. The principle according to the invention can naturally be varied within the scope of protection defined by the claims, regarding for example implementation details and fields of use. In particular, it should be noted that said couplings of the body&#39;s inlets can of course be made independently of the body to any actuator or actuator outlet and those presented above are mere examples. In addition, the body&#39;s inlets, outlets, lines and channels, for example the first external channel PK 1 , are depicted in the figures at certain locations, but it should be appreciated that these may naturally be located elsewhere in the body, nor are these by any means confined in said locations of the body by the invention and claims. Moreover, for example the cartridge chamber is most preferably implemented as a bore (cartridge bore or spindle bore, for example a solenoid valve cartridge bore or spindle bore). 
     It is further notable that the body of the invention along with its functions can be most preferably implemented with three control elements, but is should be appreciated that, alternatively (or additionally), in connection with the second inlet D 2  can also be provided a fourth cartridge chamber (MK 4 ,  FIG. 3 ) for a fourth control element (M 4 ,  FIG. 3 ) working independently of the other control elements for conducting a pressure flow from the actuator (E 2 ) coupled with the second inlet fitting (D 2 ) back into the second main line (P 2 ). In this case, the solution would have the body provided also with a fourth channel (K 4 ,  FIG. 3 ) between the second main line (P 2 ) and the second inlet (D 2 ), whereby the third connecting channel (YK 3 ) provided in the body between the first inlet (C 2 ) and the second inlet (D 2 ) would not be absolutely necessary because, for example in a floating position, the flow circuit VP 3  between the first inlet (C 2 ) and the second inlet (D 2 ) could be arranged by way of the second pressure line (P 2 ) (VP 3 ′ in  FIG. 3 ) (in a corresponding manner and analogously to the way that VP 3  circles by way of the first pressure line (P 1 ) between the first outlet (C 1 ) and the second outlet (D 1 )). In practice, the fourth channel (K 4 ), the fourth control element (M 4 ), as well as the optional third flow circuit VP 3 ′ are unnecessary as the functions can be carried out e.g. by using the third connecting channel (YK 3 ) and with fewer accessories (e.g. a fourth valve) as described elsewhere in this document. 
     It should still further be noted that the third connecting channel (YK 3 ) makes possible a flexible discharge of pressure shocks, which would not be possible should the body or the mechanism only include the control elements M 3  and M 4 , which are closed in the pressure shock situation. Thus, the pressure shock would not be able to discharge along the optional third flow circuit VP 3 ′ (by way of the main line P 2 ). 
     Still further, according to one optional embodiment, the first connecting channel (YK 1 ) can be provided as such a large (extensive) conduit that no separate cross-boring, i.e. in other words no separate second connecting channel (yk 2 ), is needed. Hence, it is to be appreciated that, although a separate second connecting channel (YK 2 ) is discussed in this document, this can be implemented solely with a first connecting channel (YK 1 ) whenever the latter reaches the pertinent objects such as for example fittings and channels.