阅读说明：本技术 筒体流速调整组件和具有双重调整标度的液压流速控制阀 (Barrel flow rate adjustment assembly and hydraulic flow rate control valve with dual adjustment scales ) 是由 S·莫利纳 G·鲁加 于 2020-02-24 设计创作，主要内容包括：本发明涉及一种用于液压阀(100)的筒体流速调整组件(10),包括：筒体本体(12)；阀杆(14),所述阀杆(14)滑动地设置于所述筒体本体(12)中；闸板(16),所述闸板(16)抵着通路开口(114)滑动地放置；套筒(20),所述套筒(20)旋转地设置于所述阀内侧,并且提供有至少一个第一开口(22)以用于允许根据第一标度而调整所述流体流速的第一值范围内的所述阀的最大流速；其中所述套筒(20)包括至少一个第二开口(22’),所述至少一个第二开口(22’)形成于所述壁中并且允许根据第二标度而调整所述流体流速的第二值范围内的所述阀的最大流速。本发明还涉及一种液压控制阀(100),所述液压控制阀(100)包括筒体流速调整组件(10)。(The present invention relates to a barrel flow rate adjustment assembly (10) for a hydraulic valve (100), comprising: a cylinder body (12); a valve stem (14), the valve stem (14) slidably disposed in the cartridge body (12); a shutter (16), the shutter (16) being slidingly placed against the passage opening (114); a sleeve (20), said sleeve (20) being rotatably arranged inside said valve and being provided with at least one first opening (22) for allowing adjustment of a maximum flow rate of said valve within a first range of values of said fluid flow rate according to a first scale; wherein the sleeve (20) comprises at least one second opening (22'), said at least one second opening (22') being formed in the wall and allowing to adjust the maximum flow rate of the valve within a second range of values of the fluid flow rate according to a second scale. The invention also relates to a hydraulic control valve (100), the hydraulic control valve (100) comprising a barrel flow rate adjustment assembly (10).)

1. A barrel flow rate adjustment assembly (10) for a hydraulic valve (100), comprising:

-a cartridge body (12);

-a valve stem (14), said valve stem (14) being slidingly disposed in said cartridge body (12), having a first end (14');

-a shutter (16), said shutter (16) being integral with a first end of said valve stem (14) and said shutter (16) being slidingly placed against a passage opening (114) of said valve (100) for adjusting the flow rate when said adjustment assembly is mounted to said hydraulic valve (100);

-a substantially cylindrical sleeve (20), said substantially cylindrical sleeve (20) being configured to be rotatably arranged inside the valve for facing a passage gap (116) when the adjustment assembly is mounted to the hydraulic valve (100), and being provided with at least one first opening (22), said at least one first opening (22) being formed in a wall (24) of the sleeve (20) and being shaped to allow adjustment of a maximum flow rate of the valve within a first range of values of the fluid flow rate according to a first scale;

characterized in that said sleeve (20) comprises at least one second opening (22'), said at least one second opening (22') being formed in said wall and allowing to adjust the maximum flow rate of said valve within a second range of values of said fluid flow rate according to a second scale.

2. The cartridge assembly (10) of claim 1 wherein a first resolution is associated with the first scale and a second, different resolution is associated with the second scale.

3. The cartridge assembly (10) of claim 1 wherein said at least one first opening (22) and said at least one second opening (22') are formed on diametrically opposed portions of said wall (24).

4. The cartridge flow rate adjustment assembly (10) of claim 1, comprising an indexing reference instrument (30), the indexing reference instrument (30) configured to graphically represent the first scale and the second scale.

5. The cartridge assembly (10) of claim 4 wherein said reference means (30) is divided into at least two parts and comprises a first indexing scale (32) and a second indexing scale (33), said first indexing scale (32) corresponding to the opening position of said at least one first opening (22) and said second indexing scale (33) corresponding to the opening position of said at least one second opening (22').

6. The cartridge assembly (10) of claim 5 wherein: the first and second indexing scales are shown on or formed directly on the cartridge assembly.

7. The cartridge assembly (10) of claim 1 wherein each of the at least one first opening (22) and the at least one second opening (22') comprises a plurality of openings formed in a wall (24) of the sleeve (20).

8. The cartridge assembly (10) of claim 1 wherein said sleeve (20) is made of plastic, polymer, or thermoplastic, metallic material, or other sintered material, or by additive manufacturing techniques.

9. The cartridge assembly (10) of claim 1 further comprising:

-an elastic element (18), the elastic element (18) being coaxially arranged on the stem (14) of the cartridge body (12) so that the stem (14) together with the shutter (16) is maintained in a monostable position with respect to the access opening (114) of the valve (100);

-a plunger element (50), said plunger element (50) being integral with said valve stem (14) and configured to slide in a chamber (13) of said cartridge body (12), said chamber (13) being coaxial with the valve stem (14) and interposed between said shutter (16) and a second end (14") of said valve stem (14);

-a compensation duct (15), said compensation duct (15) being formed in said valve stem (14) and having: a first opening (15') at a first end (14') of the valve stem (14) and at least one second opening (15"), the first opening (15') being configured to be in fluid communication with a passage opening (114) of the valve (100), the at least one second opening (15") being in fluid communication with a portion of the chamber (13) disposed between the plunger (50) and the second end (14") such that a pressure of the portion of the chamber (13) is equal to a pressure at the passage opening (114).

10. The cartridge assembly (10) of claim 1, wherein the chamber (13) is interposed between the shutter (16) and the resilient element (18), and wherein the portion of the chamber (13) is interposed between the plunger (50) and the resilient element (18).

11. The cartridge assembly (10) of claim 1, wherein the compensating conduit (15) comprises a conduit coaxial with the valve stem (14) in fluid communication with at least one conduit transverse to the stem (14) having the at least one second opening (15 ").

12. A hydraulic control valve (100), the hydraulic control valve (100) comprising a barrel flow rate adjustment assembly (10) according to any one of the preceding claims 1 to 7.

13. A hydraulic valve (100), the hydraulic valve (100) comprising a cartridge flow rate adjustment assembly (10) according to any one of the preceding claims 1 to 7, wherein the hydraulic valve (100) is a PICV or a pressure independent control valve.

Technical Field

The present invention relates to a cartridge flow rate adjustment assembly and to a hydraulic flow rate control valve with dual adjustment scales.

More particularly, the present invention relates to a cartridge flow rate pre-adjustment control assembly having a valve stem plug gate and a pre-adjustment sleeve suitable for simple type hydraulic control valves; the cartridge flow rate pre-adjustment control assembly is provided with a manual command mode or can be motorized or made thermostatic and can incorporate a dynamic balancing/compensation flow rate system.

Background

Fluid control valves (also configured for static pre-adjustment) for adjusting the flow rate of a fluid are known and widely used in hydraulic and thermal systems. The hydraulic valve is also typically provided with means for balancing or compensating for the inlet pressure and is commonly known as a pressure independent control valve or PICV.

These fluid valves are hydraulic devices that are commonly used in thermal applications where a constant flow rate of liquid fluid (typically, water) is required at the inlet (independent of the fluid pressure changes that occur upstream and downstream).

Known types of valves for dynamically adjusting and balancing the flow rate allow a more flexible and simplified design and manufacturing of hydraulic systems in which the flow rate of the fluid heat carrier towards one or more users (such as heat exchangers, radiators, fan convectors) needs to be constant. Further, the PICV allows for the adjustment of the flow rate independently of the fluid pressure conditions occurring upstream and downstream, thereby keeping a preset flow rate or a user requested flow rate constant.

The trim/balance valve or PICV generally includes three trim components: a pre-adjustment assembly of flow rate configured to pre-select a maximum nominal flow rate at an inlet of a user; a feedback regulation assembly (typically a shutter assembly) configured to regulate or block the required flow rate of the fluid heat carrier, for example as a function of the ambient temperature; and a balancing/compensation assembly configured to maintain the flow rate constant (independent of pressure conditions upstream and downstream of the valve).

PICVs typically include an actuator, such as a known glow plug provided with a push rod, that is capable of linearly actuating a valve stem (also known as a valve cartridge) to close a plug shutter in the valve body for plugging and closing the fluid passage. Typically, said actuator is realized by mechanical or electromechanical means, advantageously connected to an electronic central unit and configured to close the valve stem shutter depending on, for example, the ambient temperature. Furthermore, these valves are usually provided with an adjustment knob system, actuatable by an operator, connected to an adjustment sleeve provided with an opening configured to be rotationally varied together with the sleeve cross-section to set a desired maximum fluid flow rate value (for example, corresponding to the maximum thermal energy to be supplied).

Exemplary flow rate regulating valves are shown in documents WO-A-2018051150 and EP-A-3067772, which are also provided with an assembly for dynamically balancing the flow rate.

Another example of a valve for dynamically adjusting and balancing the flow rate of a fluid is described in european patent EP 3201500 (B1) in the name of the same applicant, which relates to a valve comprising means for adjusting the static flow rate of a fluid (which are configured to change the cross section of the passage port between the inlet and the outlet of the valve) and means for dynamically balancing the flow rate (which are configured to adjust the flow rate of the fluid leaving the valve according to the incoming fluid flow rate variations). The dynamic balancing apparatus includes a perforated element interposed between the inlet opening and the intermediate chamber to allow the fluid pathway to pass through only at least one opening of the perforated element. Furthermore, an elastic element is provided at the surface of the perforated element facing the fluid inlet opening in the valve body, so that the increase in the pressure difference between the valve inlet and outlet is matched by the enlargement of the elastic element to reduce the passage area of the opening of the perforated element and ensure a constant flow rate.

A serious drawback of these cited valve types is that each standardized valve size is characterized by a corresponding flow rate range within which the adjustment is performed. Therefore, valve manufacturers must provide many versions of the same type and size of valve, each with a different preset assembly according to the flow rate range within which the valve must operate. This fact leads to the manufacture and storage of a large number of elements and also to the sale of many types of identical valves, which differ from one another only with respect to the pre-adjustment sleeve.

Disclosure of Invention

The object of the present invention consists in overcoming and eliminating, at least in part, the operative drawbacks and limitations of the prior art given above. More particularly, an object of the present invention includes providing a bowl flow rate adjustment assembly and a corresponding hydraulic valve (e.g., of the PICV type) that can be configured and selected for operation at different flow rate ranges: a range with a larger flow rate level and a range with a smaller flow rate level.

Another object of the present invention consists in providing a cartridge flow rate adjustment assembly and a corresponding hydraulic valve (for example of the PICV type) which have a high level of reliability and durability and which, moreover, can be easily and economically manufactured.

In addition, it is an object of the present invention to provide a bowl flow rate adjustment assembly and a corresponding hydraulic valve (e.g., of the PICV type); the barrel flow rate adjustment assembly and corresponding hydraulic valve can be operated with a small size economical actuator for the same force required to cause valve closure as compared to known devices.

One object of the present invention is a cartridge flow rate adjustment assembly according to claim 1, and specific embodiments thereof are described in the dependent claims 2 to 11. According to another aspect, the invention is directed to a hydraulic valve according to claim 12 and preferred embodiments thereof according to claim 13.

Drawings

The structural operating characteristics of the cylinder flow rate adjustment assembly and of the corresponding hydraulic valve, object of the present invention, can be better understood with reference to the following detailed description, which refers to the accompanying drawings which represent some preferred non-limiting examples, in which:

FIG. 1 is a schematic isometric view of a hydraulic PICV including a bowl flow rate adjustment assembly that is the subject of the present invention;

FIG. 2 is a schematic illustration of an isometric exploded view of a hydraulic PICV including a bowl flow rate adjustment assembly that is the subject of the present invention;

FIG. 3 is a schematic diagram of an isometric exploded view of the barrel flow rate adjustment assembly of the hydraulic valve that is the subject of the present invention;

FIG. 4 is an isometric view of another perspective of the barrel flow rate adjustment assembly of the hydraulic valve that is the subject of the present invention;

FIG. 5 is a schematic diagram of a plan view of a hydraulic PICV including a cartridge flow rate adjustment assembly that is the subject of the present invention;

FIG. 6 is a schematic illustration of a cross-sectional view taken on plane VI of FIG. 5 in accordance with a hydraulic PICV that includes a barrel flow rate adjustment assembly that is the subject of the present invention;

FIG. 7 is a schematic illustration of a cross-sectional view taken on plane VII of FIG. 5 in accordance with a hydraulic PICV that includes a barrel flow rate adjustment assembly that is the subject of the present invention;

FIG. 8 is a schematic diagram of a plan view of a cartridge flow rate adjustment assembly that is the subject of the present invention;

FIG. 9 is a schematic illustration of a cross-sectional view of plane IX of FIG. 8 of a cartridge flow rate adjustment assembly in accordance with the objectives of the present invention;

fig. 10 is a schematic diagram of an operating profile of a hydraulic PICV including a barrel flow rate adjustment assembly of the present subject matter for adjusting fluid flow rates of different ranges and different resolutions based on the value of the pressure differential ap.

Detailed Description

Referring to the drawings and in particular to fig. 1, 2, 4, 5 and 6, a preferred embodiment of a hydraulic valve 100 of the PICV (pressure independent control valve) type is shown according to the present invention. The valve 100 includes a valve body 102, the valve body 102 including an inlet opening 104, an outlet opening 105, and an actuation opening 106. An opening 108 is formed in the valve body 102 (particularly in the PICV version) and a dynamic balancing/compensating pressure assembly 200, known per se, is received in the valve body 102.

Such a balancing assembly 200 generally comprises a tubular element 202, the tubular element 202 being slidingly actuated by a flexible diaphragm 204 (for example made of an elastic material), the flexible diaphragm 204 being sensitive on one of its faces to the fluid pressure in the inlet opening 104 and on its opposite face to the fluid pressure in the outlet opening 105, so that the tubular element 202 increases or restricts the fluid flow in the valve according to the pressure difference Δ P between the inlet opening 104 and the outlet opening 105. Further, the counterbalance assembly 200 generally further includes a resilient element 206, the resilient element 206 configured to maintain the tubular element 202 in a monostable position (e.g., an operational position).

Typically, the valve body 102 also includes one or more service openings 110, the service openings 110 configured to service and control the valve 100 when installed; the service opening 110 is normally closed by a plug 110'.

The valve 100 is provided with an inner wall 112 having a passageway opening 114, the passageway opening 114 being adapted for use with the cartridge flow rate adjustment assembly 10 and the counterbalance assembly 200.

Generally, the valve 100 may also be provided with conventional connectors 300 placed at the inlet opening 104 and the outlet opening 105.

The figures (in particular, fig. 3, 4, 8 and 9) show a cartridge flow rate adjustment assembly 10, the cartridge flow rate adjustment assembly 10 including a generally cylindrically shaped cartridge body 12 that slidingly receives a valve stem 14. The cartridge flow rate adjustment assembly 10 is inserted into the valve body 102 at the actuation opening 106.

The gate 16 (e.g., a plug) attached to the first end 14' of the valve stem 14 inside the valve 100 is configured to slide against the passage opening 114 of the valve 100 to regulate fluid flow from a maximum amount to full closure by the gate 16. The second end 14 "of the valve stem 14 is exposed outside of the valve body 100 and is configured to engage a conventional mechanical or electromechanical actuator (not shown) designed to linearly move the valve stem 14 to close or open the access opening 114 by the gate 16.

The valve stem 14 is also provided with another resilient element 18 (e.g., a coil spring), the resilient element 18 being coaxially disposed about the valve stem 14 and within the cartridge body 12 to retain the valve stem 14 with the gate 16 in a normally open, monostable position relative to the opening 114 of the body 102. The valve stem 14 and the resilient element are held in place in the cartridge body 12 by a first ferrule 19.

The cartridge flow rate adjustment assembly 10 (hereinafter, briefly indicated by the cartridge 10) further comprises a generally tubular cylindrical shaped sleeve 20, the sleeve 20 being attached to the inner end of the cartridge body 12.

With particular reference also to fig. 6 and 7, said sleeve 20 is configured to regulate and restrict the fluid flow exiting the passage opening 114 in the valve body 102 and moving towards the outlet opening 105 through at least one first shaped opening 22 and at least one second shaped opening 22' formed in the cylindrical outer wall 24 of the sleeve 20 itself. The shape of the first opening 22 allows for adjustment of the maximum flow rate of the valve within a first range of values of the fluid flow rate according to a first scale. The shape of the second opening 22' allows for adjustment of the maximum flow rate of the valve within a second range of values of the fluid flow rate according to a second scale. Fig. 6 and 7 show the shutter in a non-operational transitional configuration.

A first resolution is associated with the first scale and a second, different resolution is associated with the second scale. The term "resolution" means the range of flow rates that are obtainable from a rotation of the sleeve 20 by a preset angular value.

Said first and second openings 22 and 22' of the sleeve 20 allow to preset the maximum flow rate of the fluid exiting the valve by rotating the sleeve 20 itself so as to vary the passage cross section towards the outlet opening 105.

The first and second openings 22, 22' may have an open shape at the free end of the sleeve 20 (as shown), or may be integrally circumscribed in the cylindrical wall 24. The first and second openings 22, 22' are formed on portions of the cylindrical portion 24 of the sleeve 20 that are separated by solid portions of said cylindrical wall 24 to be selectively operated (in other words, not simultaneously) to adjust the fluid flow rate. Preferably, the first shaped opening 22 and the second shaped opening 22' are formed on portions of the cylindrical wall 24 at diametrically opposed locations.

Further, each of the first and second shaped openings 22, 22' has a cross section that changes in accordance with the rotation of the sleeve 20 facing the passage gap 116 of the valve body 102. When the first shaped opening 22 faces said passage gap 116, the second opening 22' is in a non-operational mode, away from the passage gap 116 (or vice versa). Each of said first and second openings 22, 22' may in turn comprise more than one opening formed in the cylindrical wall 24, having the same or different cross-sections from each other and configured to face simultaneously or consecutively the passage gap 116.

According to the example of the figures, the first opening 22 has a larger size and the second opening 22' has a smaller size, so as to be able to preset two operating configurations of the valve 100 (alternative to each other) within two different fluid flows or flow rate ranges.

Advantageously, the sleeve 20 may be made of a plastic material, a polymer, or a thermoplastic, a metallic material, or other synthetic material, or may be made by additive manufacturing techniques. Advantageously, the sleeve 20 is attached to the cartridge body 12 by pressure snap means 25, the pressure snap means 25 being formed on the inner diameter surface of the sleeve and on the end diameter surface of the cartridge 12.

The sleeve 20 is rotatable with the shutter body 12, but may also be rotated by a plug or washer 55 of the shutter 16 integral with the valve stem 14 (by connecting an implement 56 to the valve stem 14 itself), such as, for example, a flat portion formed on the first end 14 'of the valve stem 14, the first end 14' mating with a non-circular shaped opening of the plug or washer 55, as shown in fig. 3.

Still referring specifically to fig. 3, at the second end 14", the stem is rotated together with the plug 55 by means of a conventional wrench acting on the stem 14, the plug 55 in turn rotating the sleeve 20 by means of at least one tab 57, the tab 57 matching a corresponding groove 57' formed on the inner surface of the sleeve 20.

In addition, the cartridge 10 includes indexing reference means 30, the indexing reference means 30 being on the cartridge 10 itself (e.g. a disc) or formed directly thereon. The reference instrument 30 is configured to graphically illustrate the first and second scales outside the valve 100 and is placed on the cartridge body 12.

Said reference means 30 is divided into at least two parts and comprises a first graduated scale 32 and a second graduated scale 33, the first graduated scale 32 corresponding to the opening position of the first shaped opening 22 and the second graduated scale 33 corresponding to the opening position of the second shaped opening 22'.

The barrel 10 may be stationary or rotating in the valve body 12 by a second collar 118 (fig. 2), the second collar 118 being attached at the actuation opening 106. According to another embodiment, the cartridge 10 is integral with the valve body 12.

Referring particularly to fig. 1, in the preferred embodiment of the drawings, the cartridge 10 is adjustable by a wrench acting on the second end 14 "of the valve stem 14 and configured to rotate the valve stem 14 and thus the sleeve 20 relative to the cartridge body 12 for pre-adjusting the control valve 100. Once the pre-adjustment is performed, an actuator (not shown) can be installed, provided with a linear operation or a glow plug, disposed at the actuation opening 106 of the valve 100 and configured to cooperate with the valve stem 14 of the cartridge 10.

With particular reference to fig. 6, 7 and 9, in a preferred embodiment, the valve stem 14 of the cartridge assembly 10 may further comprise a compensation conduit 15 (fig. 9), the compensation conduit 15 extending partially along the axis of the valve stem 14 itself and having an opening 15 'at the first end 14' and at least another opening 15 "at the outer diameter surface of the valve stem 14 itself. On the outer diameter surface of the valve stem 14, another opening 15 "is in fluid communication with the chamber 13 formed in the cartridge body 12.

The compensating duct 15 may be curved in shape.

The inside of said chamber 13 receives, through a central hole 52, a plunger 50 integral with the valve stem 14, so that it slides with it inside said chamber 13. The plunger 50 is attached to the valve stem 14 by fixing means 54, the fixing means 54 comprising for example elastically deformable snap-in means. In particular, the fixing means 54 comprise one or more diametric collars formed on the inner surface of the central hole 52 and cooperating with other lateral collars 17, the lateral collars 17 being formed on the lateral outer surface of the stem 14. Further, plunger 50 is prevented from translating axially toward first end 14' of ram 16, and ram 16 is attached to the same end of valve stem 14. For example, the shutter 16 may advantageously be disposed on the valve stem 14 by a plug or spacer 55, the valve stem 14 being configured to move the shutter 16 into abutment with the cartridge body 12.

Advantageously, the plunger 50 is made of a plastic material, thermoplastic, polymer or thermopolymer or metallic material, or other sintered material, or may be made by additive manufacturing techniques.

The opening 15 "of the compensating duct 15 may comprise a transverse hole or duct (e.g. radial) which may be through-going, in other words which extends along all the cross section of the valve stem 14 or partially in the valve stem 14 such that it is in fluid communication with the compensating duct 15 and the chamber 13 in any way. Plunger 50 is also provided with a fluid tight element 90 (e.g., a lip gasket, elastomeric O-ring), fluid tight element 90 being disposed between the inner diameter surface of central bore 52 and the outer diameter surface of valve stem 14, and between the outer diameter surface of plunger 50 and the inner diameter surface of chamber 13.

In particular, the further opening 15 "is in fluid communication with a portion 13 'of the chamber 13, the portion 13' being interposed between the plunger 50 and the second end 14" of the valve stem 14. More particularly, such a portion 13' (on which the further opening 15 "is formed) of the chamber 13 is interposed between the plunger 50 and the elastic element 18. It is observed that the portion 13' is always fluid tight with respect to the passage opening 114.

Advantageously, said sealing element 90 may be received in a suitable annular housing or recess formed on the outer surface of the plunger 50 and the valve stem 14.

Advantageously, the cartridge 10 may be provided with a sealing element 95 to ensure fluid tightness between the cartridge 10 itself and the valve body 12.

The operation described below can be understood from the description given in advance of the valve 100.

The cartridge 10 inserted into the valve 100 of the present description has the advantageous characteristics of a sleeve 16, the sleeve 16 being capable of allowing the valve 100 to operate at different or very different flow rate scales, different sizes from one another. For example, it is possible to operate with the same valve and the same internal components depending on the configuration for high fluid flow applications and low fluid flow.

More particularly, during the installation step, by rotating the cylinder 10 and the sleeve 20 integral therewith via the wheel 400, the operator can configure the valve according to a pre-selected configuration. For example, by rotating the wheel 400 and the cartridge 10 according to the first indexing scale 32 by different degrees of openness corresponding to different positions of the first shaped opening 22 facing the access gap 116, the operator selects an operating range corresponding to this configuration. With such a configuration, the second shaped opening 22' is inoperative away from the access gap. Similarly, the operator may configure the valve 100 to operate with the second shaped opening 22' facing the access gap 116 by rotating the wheel 400 on the second indexing scale 33.

With respect to each of the first and second indexing scales 32 and 33, different positions of the cartridge 10 correspond to different selected flow rates from the smallest to the largest associated with the two different operating configurations. When the sleeve 20 is switched from one configuration to the other, it is placed in a non-operative intermediate position that is clearly different from the two operative configurations. The term non-operative position means a position in which the outer cylindrical portion 24 faces the passage gap 116 without requiring an adjusted configuration of the first and second openings 22, 22' (wherein the fluid passage is not available or only a limited fluid passage is available). Generally, setting a minimum value of the configuration range on one of the graduated scales 32 and 33 causes the fluid flow rate to never fully occlude.

With particular reference to fig. 1, 6 and 7, if the valve 100 is to be closed by the shutter 16, an electromechanical actuator (not shown) acts on the second end 14' of the valve stem 14, pushing it downwards, overcoming the force of the further resilient element 18 for moving the shutter 16 into contact with the edge of the passage opening 114, thereby blocking the fluid passage between the inlet opening 104 and the outlet opening 105.

During the closing step of the shutter 16, the chamber 13 in fluid communication with the passage opening 114 through the compensation duct 15 causes the pressure P1 of the fluid flowing through the passage opening 114 or at the passage opening 114 to be equal to the pressure P2 in the chamber 13. Thus, a force F2 is generated acting on the surface of the plunger 50 facing the chamber 13, the force F2 being opposite to the force F1 exerted by the pressure P1 of the flowing fluid, thereby compensating it. This allows the shutter 16 to be actuatable by the corresponding valve stem 14 by means of a reduced force of the electromechanical actuator, which is mainly generated by the further elastic element 18, the further elastic element 18 generally remaining constant as the pressure P1 increases.

The opening 15' of the compensation bore 15 is moved to a position adjacent to the closing shutter 16 at the passage opening 114 so that the same pressure opposite to the closing of the shutter 16 is transferred to the chamber 13. This feature allows an accurate compensation by forces of the same magnitude, which are exerted on the surface of the plunger 50 facing the chamber 13, which neutralizes the forces acting on the shutter 16.

Fig. 10 shows in particular a graph in which the actual value of the fluid flow rate in l/h (liters/hour) is a function of the range of values of the pressure difference ap between the inlet opening 104 and the outlet opening 105 of the valve 100, expressed in kPa (kilopascals). As can be seen from the values shown, rotating the sleeve (20) through the first and second openings 22, 22' results in two different adjustment ranges shown in FIG. 10 at low flow rates I (50-400l/h) and high flow rates II (200-. In addition to different flow rates with different resolutions between one level and another of the two ranges, the roman numerals 1 to 4 selectable by the first and second indexing scales 32, 33 are also different from each other. While range I matches a resolution of about 100l/h, range II matches a resolution of about 200 l/h.

The advantages obtained of the valve for hydraulically regulating and balancing the flow rate of a fluid, object of the present invention, are evident from the preceding description.

The cartridge assembly and corresponding hydraulic valve 100 are particularly advantageous; since they allow to obtain a valve that is adjustable according to two different flow rate ranges, partially overlapping each other or totally different from each other; and allows for balancing of flow rates over a range of Δ P values for both ranges.

Another advantage of the valve is that it implements one type of device or one valve for each standardized size, without the need to provide the same valve for both types; these two versions differ only with respect to the pre-adjustment range of the flow rate (available to the sleeve 20), thereby obtaining manufacturing, storage and marketing savings, since only a single type of off-the-shelf valve is required due to the standard size connection.

The present invention is also particularly advantageous because the user is provided with a hydraulic valve 100 having a conventional thermostatic plug shutter or having pressures balanced to ensure better resolution of fluid flow rate pre-adjustment, as it can operate between two ranges having two scales of different values. In fact, the valve 100 according to the invention allows to make the hydraulic system (in which it is installed) more versatile and more adaptable to possible later expansions that are required for increasing the available flow rate or generally for varying conditions (due to, for example, design errors or not taking into account parameters), without having to replace the valve 100.

The cartridge assembly and the corresponding hydraulic valve 100 object of the present invention are also advantageous in the embodiment of the figures, since they compensate for the forces acting on the shutter during the closing step, allowing the use of smaller and economical actuators and with a lower power consumption with respect to those used according to the prior art. It is observed that the use of a small-sized actuator is also advantageous from a size point of view, since it allows to install the valve in narrow spaces and boxes. Furthermore, the use of a conduit extending inside the valve stem does not compromise the travel of the valve stem itself. Another advantage of the described structure is that the compensation pressure in the chamber 13 is precisely the pressure acting on the shutter 16 at the passage opening 114 of the valve 100. The fluid flow pressure at the passageway opening 114 is in fact slightly less than the rest of the valve due to the venturi effect. The fluid connection between the passage opening 114 and the chamber 13 (through the compensation conduit 15) ensures a perfect balance of the forces generated by the pressure on the plunger 50 and also an accurate closure of the feedback by the electromechanical actuator (such as, for example, a glow tip).

Although the invention described above has been described with particular reference to some preferred embodiments, given by way of illustration and not limitation, many modifications and variations will be apparent to those skilled in the art in light of the above discussion. Accordingly, the invention is intended to embrace all such modifications and variations as fall within the scope of the appended claims.