RU2522834C2 - Gas cleaner - Google Patents

Abstract

FIELD: process engineering.

SUBSTANCE: set of inventions relates to separator designed to separate the mix of different-density substances such as gas and fluid and to method of its assembly. Proposed gas cleaner comprises the case, rotor assembly, fluid flow passage, ledge extending upward from said case and around said passage, and branch pipe. Note here that said branch pipe can get in contact with said ledge so that its inner surface abuts on ledge curves surface to produce curved flow path surface.

EFFECT: more efficient separation.

2 cl, 41 dwg

Description

The present invention relates to a separator and, in particular, but not exclusively, to a centrifugal separator for purifying a gaseous fluid.

It is well known that a mixture of fluids of different densities can be separated using a centrifugal separator. One of the specific applications of such a separator is the separation of oil from gas leaving the crankcase of an internal combustion engine.

With regard to this particular field of application of the separators, it is well understood that there is a tendency for high-pressure gases to leak out of the combustion chambers of the internal combustion engine past the corresponding piston rings into the crankcase. This continuous leakage of gas into the crankcase can lead to an undesirable increase in pressure in the crankcase and, as a result, to the need to release gas from the specified crankcase. In large freight vehicles, the exhaust gas is usually returned to the engine intake pipe. However, the gas discharged from the crankcase usually carries a certain amount of motor oil (in the form of droplets or fog) trapped from the reservoir of oil contained in the crankcase. In particular, the gas exiting between the engine cylinder and the corresponding piston tends to trap the lubricating oil located on the cylinder wall. In addition, condensation of oil vapors by the cooling system of the cylinder block forms an oil mist in the crankcase.

In order to allow the discharge of gas into the intake system without simultaneously introducing unwanted oil (especially into a turbocharging system in which the presence of coked oil can adversely affect compressor efficiency), it is necessary to clean the exhaust gas (i.e. remove oil that carries gas) before introducing gas into the intake system. This cleaning process can be carried out by a centrifugal separator, which is mounted on or near the crankcase and which directs the cleaned gas to the intake system and directs the separated oil back to the crankcase.

The centrifugal separator, which performs the task described above with significant commercial success, is the applicant's ALFDEX ™ separator. This currently used separator is described below with reference to the accompanying drawings, in detail, in order to clearly illustrate the development of the present invention, which is described later.

There are a number of problems associated with the existing ALFDEX ™ separator. These three issues can be divided into three broad categories.

Firstly, fluid paths through which the separator causes an increase in pressure are lost, which negatively affects the throughput of the separator and, therefore, the size of the engine with which the separator can be used. The first category of problem that is associated with an existing ALFDEX ™ separator can therefore be considered as related to pressure loss in the fluid path.

Secondly, the layout of the existing separator is such that, under certain conditions, the purified gas may become contaminated before leaving the separator. Accordingly, the second category of problems associated with the existing separator can be considered as related to undesirable contamination of the purified gas with oil.

Thirdly, some manufacturing techniques and design features associated with an existing separator can cause assembly difficulties and / or reliability problems. In this case, the third category of problems associated with the existing separator can be considered as related to the manufacture and reliability of the separator.

Each of these categories will be discussed in more detail below.

UA 3205

A first aspect of the present invention provides a gas treatment separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the interior space, and

at least one blade element (116 '), placed in the specified space and capable of rotating about an axis (64') so as to impart rotation to the mixture of substances intended for separation;

characterized in that the leading edge (310) part of one or each blade element (116 ') contains a guide surface, so that in use, a mixture of substances flowing in the direction of the specified leading edge (310) part is guided by the guide surface in the direction of alignment with the blade element (116 ').

Other features of the invention are applied in a separator as listed below:

A separator (2 ') as described above with respect to the first aspect of the invention, the separator (2') comprising a plurality of said blade elements (116 ') spaced at regular intervals around a specified axis (64').

A separator (2 ') as described above with respect to the first aspect of the invention, the separator (2') comprising twelve of said blade elements (116 ') spaced at equal intervals around said axis (64').

A separator (2 ') as described above with respect to the first aspect of the invention, said guide surface comprising a curved portion.

A separator (2 ') as described above with respect to the first aspect of the invention, said guide surface provided with a guide vane (314) extending from said leading edge (310) portion.

A separator (2 ') as described above with respect to the first aspect of the invention, wherein the guide vane (314) of the blade member (116') is angled (322) to the blade member (116 ') so that at a given rotation speed of the blade element (116 ') around the specified axis (64') and at a given flow rate of the specified mixture, the guide vane (314) is essentially aligned with the flow of the mixture.

A separator (2 ') as described above with respect to the first aspect of the invention, wherein the separator (2') comprises at least one separator disk (82 ') that can rotate about the specified axis (64') and fits in the space so that take these substances from the blade element (116 ').

A separator (2 ') as described above with respect to the first aspect of the invention, the separator (2') comprising a plurality of separator disks (82 ') placed by a stack (84'), rotated about one axis (64 ') and placed in the indicated space so to receive these substances from the blade member (116 ').

The separator (2 ') indicated above in relation to the first aspect of the invention, in which the specified axis (64') of each separator disk (82 ') coincides with the specified axis (64') of the blade element (116 ').

UA 3198

A second aspect of the present invention provides a gas purification separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84', 86 '), designed to impart a rotational movement to the specified mixture of substances, and the rotor assembly (78', 84 ', 86') is placed in the specified internal space and can rotate around the axis (64 ') relative to a casing (4 '), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the input (600) and the output (604), and the output (604) is located more radially in an outward direction from said axis (64 ') than the inlet (600); and

a casing member (72 ′) defining a region (606) for receiving the fluid discharged from the rotor assembly (78 ′, 84 ′, 86 ′) and directing said fluid toward the first outlet (10 ′) of the casing (4 ′) , 70 ');

characterized in that the entrance (610) to the specified area (606) contains at least one longitudinal section (612) of greater depth (613) than other longitudinal sections of the specified entrance (610).

Other features of the invention are presented in the separator below:

A separator (2 ′) as described above with respect to the second aspect of the invention, wherein said casing element (72 ′) is placed next to the end element (86 ′) of the rotor assembly (78 ′, 84 ′, 86 ′), said region (606 ) is limited between the end element (86 ') and the casing element (72').

A separator (2 ′) as described above with respect to the second aspect of the invention, wherein said entry (610) into said region (606) is limited by an end element (86 ′) and an edge around the perimeter (274) of the casing element (72 ′).

The separator (2 ') indicated above with respect to the second aspect of the invention, wherein said perimeter edge (274) is circular, so that the longitudinal portions of the inlet (610) to the specified area are circumferential along the specified edge (274).

A separator (2 ') as described above with respect to the second aspect of the invention, wherein said or each longitudinal portion (612) of greater depth (613) is provided with a recess in said edge around the perimeter (274), creating a greater distance between said edge (274) and an end member (86 ') along said or each longitudinal portion (612) than between said edge (274) and an end member (86') along said other longitudinal sections.

A separator (2 '), indicated above with respect to the second aspect of the invention, in which the circumferential edge around the perimeter (274) of the casing element (72') is concentric with the specified axis (64 ').

A separator (2 ') as described above with respect to the second aspect of the invention, wherein said or each longitudinal section (612) of greater depth (613) has a partially circular shape passing through an arc (280) from 45 ° to 110 ° and preferably 80 ° .

The separator (2 ') indicated above with respect to the second aspect of the invention, wherein said other longitudinal sections have a depth of one tenth to half the depth of said at least one longitudinal section (612) and preferably have a depth equal to one third of the depths of the at least one longitudinal portion (612).

A separator (2 ′) as described above with respect to the second aspect of the invention, wherein said at least one longitudinal portion (612) is placed on the opposite side of the casing member (72 ′) with respect to said first outlet (10 ′) of the casing (4 ′, 70 ').

A separator (2 ') as described above with respect to the second aspect of the invention, wherein said at least one longitudinal portion (612) opens into a path (272) defined by a housing member (72') in order to direct the fluid in the direction of said the first outlet (10 ') of the casing (4', 70 ').

The separator (2 ') indicated above with respect to the second aspect of the invention, wherein said at least one longitudinal section (612) is an entrance (282) to said path (272), said path (272) comprising elements (276, 278) ) at the indicated path input (282), which during use align with the direction of the fluid flowing to the specified path input (282).

The separator (2 ') indicated above with respect to the second aspect of the invention, in which said elements (276, 278) are curved at said path inlet (282), and subsequently straighten further towards the first outlet (10') of the casing (4 ', 70').

The separator (2 ') indicated above with respect to the second aspect of the invention, wherein said elements (276, 278) form opposite side walls defining said path (272).

The separator (2 '), indicated above in relation to the second aspect of the invention, in which the casing element (72') is placed next to the end element (86 ') of the rotor assembly (78', 84 ', 86') by the indicated region (606) and by (272) bounded between the end element (86 ') and the casing element (72').

The separator (2 ') indicated above in relation to the second aspect of the invention, in which the distance between the casing element (72') and the specified end element (86 ') of the rotor assembly (78', 84 ', 86') is greater in one section of the specified area (606) than in other parts thereof, wherein said one portion thus limits the indicated path (272) in the casing member (72 ').

The separator (2 ') indicated above with respect to the second aspect of the invention, wherein said path (272) comprises a tubular portion.

UA 3198

A third aspect of the present invention provides a gas purification separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and

a casing member (72 ′) defining a region (606) for receiving fluid discharged from the rotor assembly (78 ′, 84 ′) and directing said fluid towards the first outlet (10 ′) of the casing (4 ′, 70 ′ );

characterized in that said region (606) comprises a path (272) extending from one edge portion along the perimeter (274) of the casing element (72 '), said region restricting entry (282) into said path (272).

Other features of the invention are presented in the separator below:

The separator (2 ') indicated above with respect to the third aspect of the invention, wherein said path (272) contains elements (276, 278) at said path inlet (282), which during use align with the direction of fluid flow at said path inlet (272).

The separator (2 ') indicated above with respect to the third aspect of the invention, wherein said elements (276, 278) are curved at said path inlet (282) and sequentially straightened further towards the first outlet (10') of the casing (4 ', 70').

The separator (2 ') indicated above with respect to the third aspect of the invention, wherein said elements (276, 278) form opposite side walls defining said path (272).

A separator (2 ') as described above with respect to the third aspect of the invention, wherein said path inlet (282) is placed on the opposite side of the housing element (72') with respect to the first outlet (10 ') of the housing (4', 70 ').

The separator (2 ') indicated above with respect to the third aspect of the invention, wherein said perimeter portion restricting the entry of the path (282) has a partially circular shape passing through the arc (280) from 45 ° to 110 ° and preferably 80 °.

The separator (2 '), indicated above with respect to the third aspect of the invention, in which the casing element (72') is placed next to the end element (86 ') of the rotor assembly (78', 84 ', 86') with the indicated region (606) and the passage (272) bounded between the end element (86 ') and the casing element (72').

The separator (2 ') indicated above in relation to the third aspect of the invention, in which the distance between the casing element (72') and the specified end element (86 ') of the rotor assembly (78', 84 ', 86') is greater in one section of the specified area (606) than in other parts thereof, wherein said one portion thus limits said passage (272) in the casing member (72 ').

A separator (2 ') as described above with respect to the third aspect of the invention, wherein said passage (272) comprises a tubular portion (270).

UA 3198

A fourth aspect of the present invention provides a gas treatment separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and

a casing member (72 ′) defining a region (606) for receiving fluid discharged from the rotor assembly (78 ′, 84 ′) and directing said fluid towards the first outlet (10 ′) of the casing (4 ′, 70 ′ );

characterized in that said region (606) comprises a path (272) having elements (276, 278) at the inlet of said path, which during use align with the direction of fluid flow into said path inlet (282).

Other features of the invention are presented in the separator below:

The separator (2 ') indicated above with respect to the fourth aspect of the invention, wherein said path (272) extends from one edge portion along the perimeter (274) of the casing member (72'), wherein said portion limits the entrance (282) of said passage (272) )

The separator (2 ') indicated above with respect to the fourth aspect of the invention, in which said elements (276, 278) are curved at said path inlet (282) and sequentially straightened further towards the first outlet (10') of the casing (4 ', 70').

The separator (2 ') indicated above with respect to the fourth aspect of the invention, wherein said elements (276, 278) form opposite side walls defining said path (272).

A separator (2 ′) as described above with respect to the fourth aspect of the invention, wherein said path inlet (282) is placed on the opposite side of the casing member (72 ′) with respect to the first outlet (10 ′) of the casing (4 ′, 70 ′).

The separator (2 '), indicated above with respect to the fourth aspect of the invention, wherein said perimeter portion restricting the entry of the path (282) has a partially circular shape passing through the arc (280) from 45 ° to 110 ° and preferably 80 °.

The separator (2 '), indicated above in relation to the fourth aspect of the invention, in which the casing element (72') is located next to the end element (86 ') of the rotor assembly (78', 84 ', 86') by the indicated region (606) and by (272) bounded between the end element (86 ') and the casing element (72').

The separator (2 ') indicated above in relation to the fourth aspect of the invention, in which the distance between the casing element (72') and the specified end element (86 ') of the rotor assembly (78', 84 ', 86') is greater in one section of this region (606) than in other parts thereof, wherein said one portion thus limits the indicated path (272) in the casing member (72 ').

The separator (2 ') indicated above with respect to the fourth aspect of the invention, wherein said path (272) comprises a tubular portion (270).

UA 3198

A fifth aspect of the present invention provides a gas purifier (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and

a casing member (72 ′) defining a region (606) for receiving fluid discharged from the rotor assembly (78 ′, 84 ′) and directing said fluid towards the first outlet (10 ′) of the casing (4 ′, 70 ′ );

characterized in that the casing element (72 ') is provided with means (264) for separating the entrance to the specified region (606) from the fluid, which during use returns back in the direction of the specified entrance after passing by the specified entrance.

Other features of the invention are presented in the separator below:

A separator (2 ') as described above with respect to the fifth aspect of the invention, wherein said release agent (264) comprises a wall.

A separator (2 ') as described above with respect to the fifth aspect of the invention, wherein said wall extends from the process downstream side of said inlet region (606) in the direction of the process relative to said fluid stream having an inlet after said region during use ( 606).

A separator (2 ′) as described above with respect to the fifth aspect of the invention, wherein said wall is separated from said casing (4 ′).

A separator (2 ') as described above with respect to the fifth aspect of the invention, wherein said wall comprises a free end (608).

A separator (2 ′) as described above with respect to the fifth aspect of the invention, wherein said free end (608) is separated (456) from said casing (4 ′, 70 ′) in an axial direction with an axial direction from 2 mm to 200 mm, and preferably a distance of 14 mm.

A separator (2 ′) as described above with respect to the fifth aspect of the invention, wherein said free end (608) is separated (456) from said casing (4 ′, 70 ′) in a direction perpendicular to said axial direction by a distance smaller than said axial distance .

The separator (2 ') indicated above with respect to the fifth aspect of the invention, wherein said wall delimits a closed loop.

A separator (2 ') as described above with respect to the fifth aspect of the invention, wherein said wall defines a truncated cone-shaped surface.

The separator (2 ') indicated above with respect to the fifth aspect of the invention, wherein said truncated cone-shaped surface has a longitudinal axis coinciding with said rotation axis (64').

A separator (2 ') as described above with respect to the fifth aspect of the invention, wherein said truncated cone-shaped surface deviates in the direction of the process relative to said fluid stream, having an inlet after said region during use (606).

A separator (2 ′) as described above with respect to the fifth aspect of the invention, in which the casing element (72 ′) comprises means (266) for supporting the casing element (72 ′) relative to the casing (4 ′, 70 ′), and supporting means (266 ) is placed after the separation means (264) relative to the specified fluid flow, having during use an inlet after the specified area (606).

The separator (2 '), indicated above in relation to the fifth aspect of the invention, in which the supporting means (266) is a wall defining a closed loop.

The separator (2 ') indicated above with respect to the fifth aspect of the invention, wherein said wall has a cylindrical shape.

The separator (2 ') indicated above with respect to the fifth aspect of the invention, wherein said wall has a longitudinal axis coinciding with said axis of rotation (64').

A separator (2 ′) as described above with respect to the fifth aspect of the invention, wherein at least one hole (454) is provided in said wall at a junction between said wall and the casing (4 ′, 70 ′).

A separator (2 ′) as described above with respect to the fifth aspect of the invention, which also comprises a second outlet opening of the casing (4 ′, 70 ′), wherein said support means (266) is placed on a fluid flow line between the second outlet and said separation means (264).

A separator (2 '), indicated above with respect to the fifth aspect of the invention, in which the second outlet is arranged concentrically with said axis of rotation (64').

A separator (2 ′) as described above with respect to the fifth aspect of the invention, wherein said release agent (264) is housed in a casing (4 ′, 70 ′) such that during use, a fluid passing through the inlet of said region (606), flows on one side of said release agent (264), and said fluid recirculates on the other side of said release agent (264).

A separator (2 ') as described above with respect to the fifth aspect of the invention, in which an exhaust passage (211) extends between the casing member (72') and the casing (4 ', 70') to transfer fluid from said region (606) to the outside the side of the casing (4 ', 70') through the specified outlet (10 '), and the outer side of the specified outlet passage (211) is separated by a gap from the casing (4', 70 '), so that the fluid flows freely around the entire outer perimeter of the specified exhaust passage (211).

A separator (2 ') as described above with respect to the fifth aspect of the invention, wherein said outlet passage (211) is separated from the casing member (72') and the casing (4 ', 70').

UA 3194

A sixth aspect of the present invention provides a gas cleaning separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

an opening for passing a fluid flow along a flow path between the outer part of said casing (4 ') and said inner space, and

a protrusion (6 ') protruding upward from the casing (4') and surrounding the specified hole;

characterized in that the protrusion (6 ') contains a curved surface (221) extending inwardly into the hole.

Other features of the invention are presented in the separator below:

A separator (2 ') as described above with respect to the sixth aspect of the invention, wherein said curved surface (221) forms a closed loop around the hole and goes inward into the hole so as to reduce the area of the hole when moving through said hole from the outside of said casing (4 ') in the direction of the indicated interior space.

A separator (2 ′) as described above with respect to the sixth aspect of the invention, wherein said curved surface (221) describes a partially circular line when viewed in cross section made in a plane coinciding with the longitudinal axis (64 ′) through said hole.

The separator (2 '), indicated above with respect to the sixth aspect of the invention, in which the protrusion (6') comprises a generally cylindrical shape (217), the free end of which is provided with a circular protrusion (219) forming a curved surface (221).

A separator (2 ') as described above with respect to the sixth aspect of the invention, which also includes a pipe (22') that can be connected to the protrusion (6 ') so that the inner surface (216) of the pipe (22') is combined with the curved surface of the protrusion (6 ') to obtain a curved surface in transit.

The separator (2 '), indicated above with respect to the sixth aspect of the invention, in which the inner surface of the nozzle (216) meets the curved surface (221) on the edge (229) of the protrusion (6') and is oriented tangentially to the curved surface at this meeting point (221).

A separator (2 ') as described above with respect to the sixth aspect of the invention, in which the pipe (22') further comprises a curved wall (235) configured to fit against the curved surface (221) of the protrusion (6 ').

A separator (2 ') as described above with respect to the sixth aspect of the invention, in which the nozzle (22') can be connected to the protrusion (6 ') for any rotation orientation.

A separator (2 ') as described above with respect to the sixth aspect of the invention, wherein the nozzle (22') can be connected to the protrusion (6 ') by friction welding.

A seventh aspect of the present invention provides a method for assembling a gas treatment separator (2 '), the method comprising the step of connecting the nozzle (22') to the protrusion (6 ') by friction welding; a separator is indicated above with respect to the sixth aspect of the present invention.

UA 3198

An eighth aspect of the present invention provides a gas cleaning separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and

a casing member (72 ′) defining a region (606) for receiving fluid discharged from the rotor assembly (78 ′, 84 ′) and directing said fluid towards the first outlet (10 ′) of the casing (4 ′, 70 ′ );

characterized in that the outlet passage (211) passes between the casing element (72 ') and the casing (4', 70 ') for transferring fluid from the specified area (606) to the outside of the casing (4', 70 ') through the specified outlet a hole (10 ′), the outer side of said outlet passage (211) being separated by a gap from the casing (4 ′, 70 ′) so that fluid can flow freely around the entire outer perimeter of said exit passage (211).

Other features of the invention are presented in the separator below:

A separator (2 ′) as described above with respect to the eighth aspect of the invention, in which the housing element (72 ′) is provided with means (264) for separating the inlet of the indicated region (606) from the fluid, which during use recirculates back to the indicated inlet after flowing past the specified entrance, and the specified output passage (211) comes from the specified separation means (264).

A separator (2 ′) as described above with respect to the eighth aspect of the invention, wherein said release agent (264) comprises a wall and said wall preferably has a free end (608) and is separated by a gap from said casing (4 ′, 70 ′).

A separator (2 ') as described above with respect to the eighth aspect of the invention, wherein said outlet passage (211) is separated from the casing member (72') and the casing (4 ', 70').

UA 3197

A ninth aspect of the present invention provides a gas cleaning separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and

a casing member (72 ') located adjacent to the rotor assembly (78', 84 '), the casing member and the rotor assembly being separated from each other so as to form a first region (606) between them on the first side of the casing member (72') wherein said first region (606) restricts the first path for fluid flow discharged from the rotor assembly (78 ', 84'); the casing element (72 ') is also separated from the casing (4') so as to form a second region between them on the second side of the casing element (72 '), said second region (614) restricting the second path for fluid flow to the fluid, released from the rotor assembly (78 ', 84');

characterized in that the rotor assembly (78 ', 84') comprises a second inlet (618), which opens into said second region (614) on said second side of the housing element (72 '), a second outlet (620) located more radially in outward from the indicated axis (64 ') than the second inlet (618) and the second flow path (616) for providing fluid communication between the second inlet (618) and the second outlet (620).

Other features of the invention are presented in the separator below:

A separator (2 ') as described above with respect to the ninth aspect of the invention, wherein said second outlet (620) opens into a fluid passage forming a fluid connection between said first outlet (604) and said first and second regions (606, 614).

The separator (2 ') specified above with respect to the ninth aspect of the invention, wherein said second outlet (620) opens at a location that, in relation to the stream of said substances discharged from said first outlet (604), is placed behind said first exit (604) and before the indicated first and second areas (606, 614).

The separator (2 ') indicated above in relation to the ninth aspect of the invention, in which the second path (616) for the flow contains the space between the first and second elements (86', 240) of the rotor assembly, each of which contains a disk-shaped part, two elements ( 86 ', 240') are centered on the indicated axis (64 ').

A separator (2 ') as described above with respect to the ninth aspect of the invention, in which the disk-shaped parts of said elements (86', 240) have each radially outer edge of a substantially circular shape, wherein two elements (86 ', 240) are placed concentrically with a friend.

A separator (2 ') as described above with respect to the ninth aspect of the invention, wherein at least one extended element (298) is placed in said space between the first and second elements (86', 240) so as to move a fluid placed in said outside from the indicated axis (64 ') when, during use, the rotor assembly rotates about the indicated axis (64').

A separator (2 ') as described above with respect to the ninth aspect of the invention, in which one or each extended element (298) extends radially along a second flow path (616).

The separator (2 '), indicated above in relation to the ninth aspect of the invention, in which one or each extended element (298) is formed by one of the first and second elements (86', 240) and adjacent to the other of the first and second elements (86 ', 240).

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said disc-shaped part of each element (86', 240) has the shape of a truncated cone.

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said second flow path (616) has the shape of a truncated cone.

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said first flow path (602) is in the form of a truncated cone.

The separator (2 ') indicated above with respect to the ninth aspect of the invention, in which the second inlet (618) of said second flow path (616) is annular and centered on said axis (64').

The separator (2 ') indicated above with respect to the ninth aspect of the invention, in which the second flow path (616) goes from the opening in the casing member (72') between the first and second sides of the casing member (72 ').

The separator (2 ') indicated above with respect to the ninth aspect of the invention, in which the second inlet (618) of said second flow path (616) is limited to a generally cylindrical wall (300).

The separator (2 '), indicated above with respect to the ninth aspect of the invention, in which there is provided a space between a part of a casing element (72') defining a specified opening therein and a first part (300) of a rotor assembly defining at least a part of said second path (616) for the flow, and in which a further portion 304) of the rotor assembly extends from said first part (300) so as to cover said space.

A separator (2 ') as described above with respect to the ninth aspect of the invention, wherein said further part (304) is located on said second side of the housing element (72').

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said further part (304) comes from the second inlet (618).

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said further part (304) has an annular shape.

The separator (2 ') indicated above in relation to the ninth aspect of the invention, wherein said further part (304) has an outer circumferential edge around the perimeter, the diameter of which is larger than the diameter of the specified hole in the casing element (72').

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said further part (304) is flat and oriented in a plane about which said axis (64') is perpendicular.

A separator (2 '), indicated above with respect to the ninth aspect of the invention, in which the surface restricting the second flow path (616) and coming from the second inlet (618) has a radially outermost part (302) relative to the specified axis (64'), which converges with the specified axis (64 ') when moving along the specified second path (616) for the flow from the second inlet (618) in the direction of the second outlet (620).

The separator (2 ') indicated above with respect to the ninth aspect of the invention, wherein said radially outermost part (302) of said surface of the second flow path has a truncated cone shape.

The separator (2 '), indicated above with respect to the ninth aspect of the invention, wherein said truncated cone shape of said radially outermost part (302) has a central longitudinal axis coinciding with said rotation axis (64').

UA 3195

A tenth aspect of the present invention provides a gas purifier (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ', 70') forming an internal space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and

a rotor assembly (78 ', 84'), which also contains a rotating shaft (78 '), coinciding with the specified axis (64') and mounted on the specified casing (4 ', 70'), in which the first end part of the rotating shaft (78 ') passes through the specified casing (4', 70 ') to a position external to the specified casing (4', 70 '), and the passage (92') for the fluid passes axially through the rotating shaft (78 ') and has an opening, placed outside of the specified casing (4 ', 70');

characterized in that the rotor assembly (78 ', 84') also contains flow control means (346, 366) designed to control the flow of fluid into the specified passage in the shaft (92 ') for the fluid from the outside of the specified casing (4 ', 70'), wherein the flow control means (346, 366) comprise means for imparting a rotational motion along the path radially outward from the shaft fluid passage (92 ') to the fluid flowing into said passage (92').

Other features of the invention are presented in the separator below:

The separator (2 ') indicated above with respect to the tenth aspect of the invention, wherein said rotational movement is centered on said rotation axis (64') of the rotor assembly (78 ', 84').

The separator (2 ') indicated above with respect to the tenth aspect of the invention, wherein said passage (92') coincides with said rotation axis (64 ') of the rotor assembly (78', 84 ').

A separator (2 ') as described above with respect to the tenth aspect of the invention, wherein said means for imparting rotational motion to said fluid comprises at least one path for fluid (366) radially outwardly relative to said rotary axis (64') of rotation node (78 ', 84').

A separator (2 ′) as described above with respect to the tenth aspect of the invention, wherein said means for imparting rotational motion to said fluid comprises an element (364) separated by a gap from said passage opening (92 ′) for the shaft fluid in which at least one fluid path (366) has an opening passing through said element (364).

The separator (2 ') indicated above in relation to the tenth aspect of the invention, in which four of the specified paths for the fluid (366) are placed at equal distances along the circumference of a circle centered on the specified axis (64').

A separator (2 ') as described above with respect to the tenth aspect of the invention, wherein said element (364) is flat and oriented perpendicular to said axis (64').

A separator (2 '), indicated above with respect to the tenth aspect of the invention, in which the flow control means also comprises at least one drain hole (368) placed further in the radial direction from the specified axis (64') compared to each path (366 ) for fluid.

A separator (2 ') as described above with respect to the tenth aspect of the invention, wherein the flow control means (364, 366) and at least a portion of the turbine (88') for driving the rotor assembly (78 ', 84') are a single component .

The separator (2 '), indicated above with respect to the tenth aspect of the invention, in which the second end portion of the rotary shaft (78'), remote from the first end portion, is mounted on the casing (4 ', 70').

A separator (2 ') as described above with respect to the tenth aspect of the invention, in which a fluid passage (92') extends between the first and second end parts of the rotary shaft (78 ') so as to provide fluid through-passage between the external and internal casing parts (4 ', 70').

A cage (2 ′) as described above with respect to the tenth aspect of the invention, wherein the fluid passage (92 ′) is in fluid communication with a bearing (50 ′) on which a second end portion is mounted in the casing (4 ′, 70 ′) rotating shaft (78 ').

A separator (2 ′) as described above with respect to the tenth aspect of the invention, wherein the fluid passage (92 ′) is in fluid communication with said inlet (600) of the rotor assembly.

UA 3223

An eleventh aspect of the present invention provides a method for assembling a gas treatment separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ', 12') defining an internal space and having an opening (8 ') therein, designed to provide fluid communication between the specified internal space and the outer side of the specified casing (4', 12 '), and

a fluid passage (22 ′) sealed around said hole (8 ′) and in fluid communication with it to transfer said fluid through said passage (22 ′) and a hole (8 ′) between said inner space and the outer side of said casing (4 ', 12');

characterized in that the method of assembly of said separator (2 ') comprises the step of:

fastening the casing material (4 ', 12') and the fluid passage (22 ') together along a closed loop by crossing the adjacent surfaces of the casing (4', 12 ') and the fluid passage.

Other features of the invention are presented in the method below:

The method described above with respect to the eleventh aspect of the invention, wherein said closed loop has a circle shape.

The method described above with respect to the eleventh aspect of the invention, wherein said bonding step comprises rotating the casing (4 ′, 12 ′) and the fluid passage (22 ′) relative to each other at the same time that said surfaces are adjacent to each other.

The method described above with respect to the eleventh aspect of the invention, wherein said relative rotation of the casing (4 ′, 12 ′) and the fluid passage (22 ′) is stopped with the casing (4 ′, 12 ′) and the fluid passage (22 ′) media placed in the required position relative to each other so as to allow said abutment surfaces to bond to each other.

The method described above with respect to the eleventh aspect of the invention, wherein said bonding step comprises friction welding of said adjacent surfaces with each other.

The method described above with respect to the eleventh aspect of the invention, wherein said bonding step comprises applying adhesive to at least one of said adjacent surfaces.

The method described above with respect to the eleventh aspect of the invention, wherein said bonding step comprises ultrasonic welding or vibration welding of said adjacent surfaces to each other.

A method as described above with respect to the eleventh aspect of the invention, wherein the fluid passageway (22 ′) is a nozzle comprising an open end remote from said abutment surface for subsequent connection to another fluid passage, such as a hose.

A twelfth aspect of the present invention provides a gas purification separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming an internal space and having an opening (8') therein, designed to provide fluid communication between the specified internal space and the outer side of the specified casing (4 ', 12'), and

a fluid passage (22 ′) sealed around said hole (8 ′) and in fluid communication with it to transfer said fluid through said passage (22 ′) and a hole (8 ′) between said inner space and the outer side of said casing (4 ', 12');

characterized in that the material of the casing (4 ', 12') and the passage (22 ') for the fluid are fastened together along a closed loop formed by the intersection of the adjacent surfaces of the casing (4', 12 ') and the passage (22') for the fluid.

Other features of the invention are presented in the separator below:

The separator (2 ') indicated above with respect to the twelfth aspect of the invention, wherein said closed loop has a circle shape.

A separator (2 ′) as described above with respect to the twelfth aspect of the invention, wherein said bonding is obtained by rotating the casing (4 ′, 12 ′) ′ and the fluid passage (22 ′) relative to each other while their surfaces are indicated adjacent to each other.

A separator (2 ′) as described above with respect to the twelfth aspect of the invention, wherein said relative rotation of the casing (4 ′, 12 ′) and the passage (22 ′) for the fluid is stopped with the casing (4 ′, 12 ′) and the passage (22 ') for a fluid placed in a desired position relative to each other so as to allow said adjacent surfaces to bond to each other.

A separator (2 ') as described above with respect to the twelfth aspect of the invention, wherein said bonding is carried out by friction welding of said adjacent surfaces with each other.

A separator (2 ') as defined above with respect to the twelfth aspect of the invention, wherein said bonding is performed by applying adhesive to at least one of said adjacent surfaces.

A separator (2 ') as described above with respect to the twelfth aspect of the invention, wherein said bonding is performed by ultrasonic welding or vibration welding of said adjacent surfaces to each other.

A separator (2 ′) as described above with respect to the twelfth aspect of the invention, wherein the fluid passageway (22 ′) is a nozzle comprising an open end remote from said adjacent surface for subsequent connection to another fluid passage such like a hose.

UA 3184

The thirteenth aspect of the present invention provides a method for assembling a gas purifier separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ′, 70 ′) comprising first and second separate parts (4 ′, 70 ′), the first casing part (4 ′) having a mounting surface (632) on which a base surface (630) of the second part (70 ') the casing so as to limit the inner surface of the casing (4', 70 '); and

a rotor assembly (78 ', 84') placed in the indicated interior space and rotating about an axis (64 ') of the first part (4') of the casing relative to the casing (4 ', 70'), the rotor assembly (78 ', 84') contains a rotating shaft (78 ') mounted rotatably in the first part (4') of the casing using a bearing assembly (50 ') and mounted rotatably in the second part (70') of the casing;

characterized in that the method of assembling said separator (2 ') comprises the steps of:

installation with the possibility of rotation of the rotating shaft (78 ') in the second part (70') of the casing in a position relative to the specified base surface (630), and the specified predetermined position coincides with the specified axis (64 ') while the base surface (630 ) the second part (70 ') of the casing is combined with the mounting surface (632) of the first part (4') of the casing;

placing the bearing assembly (50 ') in the fixture (500), the fixture (500) comprising a base surface (634) for aligning with the mounting surface (632) of the first casing part (4'), and means for receiving said bearing assembly (50) ') to a position relative to the base surface (634) of the fixture (500) so that the bearing assembly (50') is received by the fixture in position relative to the base surface (634) of the fixture that coincides with the specified axis (64 ') at that time when basic I surface (634) of the fixture (500) is aligned with the specified mounting surface (632) of the first part (4 ') of the casing;

alignment of the base surface (634) of the clamping device (500) with the specified mounting surface (632) of the first part (4 ') of the casing; and

securing the bearing assembly (50 ') on the first part (4') of the casing.

Other features of the invention are presented in the method below:

The method described above with respect to the thirteenth aspect of the invention, in which the step of securing the bearing assembly (50 ') comprises moving the receiving means (512) of the clamping device (500) in the axial direction along the specified axis (64') relative to the first part (4 ') of the casing while the base surface (634) of the fixture (500) is aligned with the indicated mounting surface (632) of the first part (4 ') of the casing, and the bearing assembly (50') is thus brought into contact with the first part (4 ') casing.

The method described above with respect to the thirteenth aspect of the invention, in which the receiving means (512) moves in the indicated axial direction relative to the base surface (634) of the clamping device (500) so as to press the bearing assembly (50 ') against the first part (4') casing.

The method described above with respect to the thirteenth aspect of the invention, in which the clamping device (500) comprises means for allowing the receiving means (512) to move axially along a specified axis (64 ') relative to the base surface (634) of the clamping device (500).

The method described above with respect to the thirteenth aspect of the invention, wherein the step of securing the bearing assembly (50 ') comprises rotating the receiving means (512) of the clamping device (500) about said axis (64') with respect to the first casing part (4 '), time as the base surface (634) of the fixture (500) is aligned with the specified mounting surface (632) of the first part (4 ') of the casing;

The method described above with respect to the thirteenth aspect of the invention, wherein the step of securing the bearing assembly (50 ') comprises friction welding of the bearing assembly (50') with the first housing part (4 ').

The method described above with respect to the thirteenth aspect of the invention, in which the clamping device (500) comprises means for allowing the receiving means (512) to rotate relative to the base surface (634) of the clamping device (500).

A fourteenth aspect of the present invention provides a gas purifying separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; wherein the separator (2 ') is assembled as described above with respect to the thirteenth aspect of the present invention.

UA 3309

A fifteenth aspect of the present invention provides a method for assembling a system comprising a gas treatment separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the method comprises the steps of selecting a particular variant of a component of the first type (4 ') from a variety of different variants of the specified component of the first type (4'); and connecting said specific embodiment of said component of the first type (4 ') with a component of the second type (12');

characterized in that the specified many different variants of the specified component of the first type (4 ') contains common features (207, 211) for connection with the specified component of the second type (12').

Other features of the invention are presented in the method below:

The method described above with respect to the fifteenth aspect of the invention, which further comprises the step of selecting a particular embodiment of a component of the second type (12 ′) from a plurality of different variations of said component of the second type (12 ′).

The method described above with respect to the fifteenth aspect of the invention, which also includes the step of placing a component of the third type between the components of the first and second types (4 ', 12').

The method described above with respect to the fifteenth aspect of the invention, which further comprises the step of selecting a third type component from a plurality of different variants of said third type component, said many different variants of the third type component containing common features for connecting to said first and second type components (4 ' , 12').

The method described above with respect to the fifteenth aspect of the invention, wherein said first type component comprises a rotor shroud (4 ′), said second type component comprises a valve assembly shroud (12 ′); and said component of the third type comprises a heat shield.

The method described above with respect to the fifteenth aspect of the invention, wherein said components are said separator (2 ').

The method described above with respect to the fifteenth aspect of the invention, wherein said plurality of different variants of said component of the first type (4 ′) comprises further general features (6 ′) for connecting to a component of the fourth type (22 ′).

The method described above with respect to the fifteenth aspect of the invention, wherein said component of the fourth type is a nozzle (22 ').

A sixteenth aspect of the present invention provides a kit for assembling a gas purifier separator (2 ′) for separating a fluid mixture of substances of different densities, such as gas and liquid; however, the specified set of parts contains many different variants of the component of the first type (4 ') of the specified separator (2') for connection with a component of the second type (12 ') of the specified separator (2'); and at least one variant of the specified component of the second type (12 '); characterized in that the specified many different variants of the specified component of the first type (4 ') contains common features (207, 211) for connection with the specified component of the second type (12'). Ideally, said many different variations of said component of the first type (4 ′) comprise further general features (6 ′) for connecting to a component of the third type (22 ′).

A seventeenth aspect of the present invention provides a gas purification separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), and

a valve assembly (14 '), designed to control the flow from the outlet (10') of the specified casing (4 ') of the substance separated from the mixture of substances, said valve assembly (14') comprising a valve device located in an internal space bounded by valve cover (12 ');

characterized in that the casing of the valve assembly (12 ') is separated from the casing of the rotor assembly (4').

UA 3199

An eighteenth aspect of the present invention provides a gas purifier (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ', 70') forming an internal space,

a rotor assembly located in said interior space and rotatable about an axis (64 ') with respect to the housing, and

the casing element (72 ') is installed in the specified casing (4', 70 ') so as to allow the passage of fluid to either side of the casing element (72'), and the fluid flowing on one side of the specified element (72 ') is directed the specified element to the outer side of the specified casing (4 ', 70') through the first outlet (10 ') of the specified casing (4', 70 ');

characterized in that said fluid is guided through an exhaust passage (211) connecting said housing element (72 ') to the outside of the housing, wherein the exhaust passage (211) is sealed with at least one of the housing elements (72') and the housing ( 4 ', 70') by means of a sealing element provided near the outlet passage (211).

Other features of the invention are presented in the separator below:

A separator (2 ′) as described above with respect to the eighteenth aspect of the invention, wherein said outlet passage (211) is spaced apart from said casing (4 ′, 70 ′).

A separator (2 ') as described above with respect to the eighteenth aspect of the invention, wherein said outlet passage (211) is separated from and sealed by a casing member (72') by means of a sealing member (215).

A separator (2 ') as described above with respect to the eighteenth aspect of the invention, wherein said outlet passage (211) is separated from and sealed by a casing member (4', 70 ') by means of a sealing member (213).

A separator (2 ') as described above with respect to the eighteenth aspect of the invention, in which one or each sealing element for securing said outlet passage (211) is placed on the outer surface adjacent to a protrusion formed by said surface.

A separator (2 ') as described above with respect to the eighteenth aspect of the invention, wherein said outlet passage (211) is integral with a valve assembly (14') located outside of the casing (4 ', 70') to control the flow of fluid from casing (4 ', 70').

A separator (2 ') as described above with respect to the eighteenth aspect of the invention, in which one or each sealing element is an annular seal.

A separator (2 ′) as described above with respect to the eighteenth aspect of the invention, wherein said outlet passage (211) is separated from said casing (4 ′, 70 ′) so as to allow fluid located between the casing element (72 ′) and said casing (4 ', 70') flow along its entire outer perimeter.

UA 3196

A nineteenth aspect of the present invention provides a gas purification separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); and in which the rotor assembly (78 ', 84') comprises a rotary shaft (78 ') having a longitudinal axis coinciding with the indicated axis of rotation (64') and a separator disk (82 ') mounted on the rotary shaft (78') by holes (252), which is placed in the separator disk (82 ');

characterized in that the rotating shaft (78 ') contains at least one slot (254), and that the hole (252) in the separator disk (82) has a shape corresponding to a transverse section made perpendicular to the axis (64') passing through a rotating shaft (78 ') and at least one slot (254).

Other features of the invention are presented in the separator below:

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein at least one slot (254) is placed on a central sleeve (114') connected to the rotary shaft (78 ').

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which three slots are provided (254).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein at least one slot (254) comprises a ridge (352) forming a free end of the slot (254) and a base (350) radially inward relative to the ridge (352) moreover, the base (250) has a larger circumference than the crest (352).

A separator (2 '), indicated above with respect to the nineteenth aspect of the invention, in which the various circumferential dimensions of the base (350) and the ridge (352) form a ledge (354) on either side of at least one slot (254) at the junction between the base ( 350) and comb (352).

The separator (2 ') indicated above with respect to the nineteenth aspect of the invention, in which the circumferential dimensions of the base (350) vary along the axial length of at least one slot (254).

The separator (2 ') indicated above in relation to the nineteenth aspect of the invention, in which the separation disk (82') has the shape of a truncated cone.

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which one or each splines extends axially along the length of the rotating shaft (78').

Fretting prevention

A twentieth aspect of the present invention provides a gas purification separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the specified mixture of substances, the rotor assembly (78 ', 84') located in the indicated internal space and able to rotate around an axis (64 ') relative to the casing (4'), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and output (604) is located more radially in outward from the specified axis (64 ') than the inlet (600); in which the rotor assembly (78 ', 84') also contains a rotating shaft (78 ');

characterized in that said rotating shaft (78 ') is provided with a plastic coating along the length of said rotating shaft (78'), taking at least one component of said separator (2 ') while sliding.

A separator (2 ') as described above with respect to the twentieth aspect of the invention, wherein at least one of said components is made of a metal material.

The separator (2 ') indicated above in relation to the twentieth aspect of the invention, in which at least one of these components is a coil spring.

A cage (2 ') as described above with respect to the twentieth aspect of the invention, wherein at least one of said components is a bearing assembly (50').

A separator (2 ′) as described above with respect to the twentieth aspect of the invention, wherein said rotary shaft (78 ′) receives two said components at opposite end portions of said rotary shaft (78 ′) where each component is a coil spring (130 ′, 96 ′) )

A cage (2 ') as described above with respect to the twentieth aspect of the invention, in which each coil spring (130', 96 ') is compressed between the rotor assembly (78', 84 ') and, in addition, one of the two bearing assemblies (50' , 90 ') connecting the rotating shaft (78') with the casing (4 ').

The separator (2 ') indicated above with respect to the twentieth aspect of the invention, in which each coil spring (130', 96 ') is made of a metal material.

The separator (2 ') specified above in relation to the twentieth aspect of the invention, in which the specified rotating shaft (78') is made of non-hardened material.

The separator (2 ') indicated above in relation to the twentieth aspect of the invention, in which the specified material is unhardened metal and preferably non-hardened steel.

The separator (2 ') specified above in relation to the twentieth aspect of the invention, in which the rotor assembly (78', 84 ') contains at least one element (114', 116 ', 254), coming from the specified rotating shaft (78'), in which the specified element (114 ', 116', 254) is made of the same material as the specified coating, and is made as a whole with it.

The separator (2 ') indicated above with respect to the twentieth aspect of the invention, wherein said coating and said at least one element (114', 116 ', 254) are injection molded on said rotary shaft (78') and thus formed simultaneously with another.

UA 3291

A twenty-first aspect of the present invention provides a gas cleaning separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid; the separator (2 ') contains:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84'), designed to impart a rotational motion to the mixture of substances, the rotor assembly (78 ”, 84 ') is located in the specified internal space and is able to rotate around an axis (64') relative to the casing (4 '), wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604),

characterized in that the separator (2 ') also contains an electric motor (380) for rotating the rotor assembly (78 ”, 84') and a passage for the fluid through the electric motor (380) for receiving when using a substance separated from the mixture of substances.

Other features of the invention are presented in the separator below:

A separator (2 ') as described above with respect to the twenty-first aspect of the invention, wherein said fluid passage through an electric motor (380) is at least partially limited by a rotor (382) and a stator (400) of an electric motor (380).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said fluid passage comprises a space between the rotor (382) and the stator (400) of the electric motor (380).

A separator (2 ′) as described above with respect to the nineteenth aspect of the invention, wherein said rotor (382) is connected to the rotor assembly (78 ″, 84 ′).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which electrical wires placed in the indicated fluid path are sealed with an insulating material.

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said insulating material is provided as a layer covering the electrical wires of said stator (400).

A separator (2 ') as defined above with respect to the nineteenth aspect of the invention, wherein said insulating material comprises epoxy varnish.

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which the electric motor comprises one or more electronic components isolated from said fluid passage through the electric motor (380).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which the separator (2') comprises a casing (384) in which an electric motor (380) is placed.

A separator (2 ′) as described above with respect to the nineteenth aspect of the invention, wherein said motor case (384) is connected and can be separated from the case (4 ′) in which the rotor assembly (78 ”, 84 ′) is housed.

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which the casing of the electric motor (384) comprises a compartment isolated from said passage for the fluid and in which the electronic components (408) of the electric motor (380) are placed.

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said compartment has a generally annular or partially annular shape, which in the separator assembly (2') is concentric with the indicated rotor assembly (78 ”, 84 ′).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said compartment is covered by said motor case (384) and an element (394) separated from and isolated from said case (384).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said element (394) has a generally annular or truncated cone shape.

A separator (2 ′) as described above with respect to the nineteenth aspect of the invention, wherein said element (394) is placed concentrically with said rotor assembly (78 ″, 84 ′).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein the radially inner part of said element (394) is isolated from said motor casing (384) along a closed loop and the radially outer part of said element (394) is isolated from said motor casing ( 384) along another closed loop.

The separator (2 ') indicated above with respect to the nineteenth aspect of the invention, wherein said radially inner part of said element (394) is isolated from the generally cylindrical part (392) of said electric motor casing (384) into which said rotary rotor passes knot (78 ”, 84 ').

The separator (2 ') indicated above with respect to the nineteenth aspect of the invention, wherein said radially inner part of said element (394) defines an opening, has a diameter that is less than or substantially equal to the inner diameter of the stator (400) of the electric motor (380).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said element (394) is provided with at least one hole through which an electric wire is passed and in which said wire is insulated.

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said one or more electronic components comprise one or more components for monitoring the operation of an electric motor (380).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, wherein said fluid passage is in fluid communication with an outlet (402) in an electric motor case (384).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, which also includes an electrical connector (412) for receiving an electric wire supplying electric current and / or control signals to an electric motor (380).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which the electrical connector (412) is electrically connected to the electric motor (380) via one or more electrical components (408).

A separator (2 ') as described above with respect to the nineteenth aspect of the invention, in which an electrical connector (412) is placed in an opening through a portion of the casing (384) of the separator (2').

A twenty-second aspect of the invention provides a gas treatment separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid, comprising:

a casing (4 ') forming the inner space,

a rotor assembly (78 ', 84') designed to impart a rotational motion to the mixture of substances, the rotor assembly (78 '', 84 ') located in the indicated inner space and able to rotate around an axis (64') relative to the casing (4 ') wherein the rotor assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which said substances are discharged from the rotor assembly during use, and a flow path (602) for providing fluid communication between the inlet (600) and output (604), and the separator further comprises an ele ctromotor (380) for rotating the rotor assembly (78``, 84 ') and the passage for the fluid through the electric motor (380) for receiving, when using, a substance separated from the mixture of substances, characterized in that the passage for the fluid through the electric motor (380) is limited, at least in part, by the rotor (382) and the stator (400) of the electric motor (380), and the electrical wires are located in the specified passage for the fluid, insulated with insulating material.

Preferably, said fluid passage comprises a space between the rotor (382) and the stator (400) of the electric motor (380).

Preferably, said rotor (382) is coupled to a rotor assembly (78 '', 84 ').

Preferably, said insulating material is provided as a layer covering the electrical wires of said stator (400).

Preferably, said insulating material comprises epoxy varnish.

Preferably, the electric motor comprises one or more electronic components isolated from said fluid passage through the electric motor (380).

Preferably, the separator (2 ') comprises a housing (384) in which an electric motor (380) is placed.

Preferably, said motor case (384) in which the rotor assembly (78``, 84 ') is placed.

Preferably, the casing of the electric motor (384) comprises a compartment isolated from said fluid passage and in which electronic components (408) of the electric motor (380) are placed.

Preferably, said compartment has a generally annular or partially annular shape, which in the separator assembly (2 ′) is concentric with said rotor assembly (78 ″, 84 ′).

Preferably, the specified compartment is covered by the specified casing of the electric motor (384) and the element (394), separated from the specified casing (384) and isolated from it.

Preferably, said element (394) has a generally annular or truncated cone shape.

Preferably said element (394) is placed concentrically with said rotor assembly (78``, 84 ').

Preferably, the radially inner part of said element 9394) is isolated from said casing of an electric motor (384) along a closed loop, and the radially outer part of said element (394) is isolated from a specified casing of an electric motor (384) along another closed loop.

Preferably, said radially inner part of said element (394) is isolated from the generally cylindrical part (392) of said electric motor casing (384) into which said rotor assembly (78 '', 84 ') passes in a separator in the bur.

Preferably, said radially inner part of said element (394) defines an opening, has a diameter that is less than or substantially equal to the inner diameter of the stator (400) of the electric motor (380).

Preferably, said element (394) is provided with at least one hole through which an electric wire is passed and in which said wire is insulated.

Preferably, said one or more electronic components comprise one or more components for monitoring the operation of an electric motor (380).

Preferably, the electrical connector (412) is electrically connected to the electric motor (380) via one or more electrical components (408).

Preferably, the electrical connector (412) is placed in an opening passing through a portion of the casing (384) of the separator (2 ').

The centrifugal separator ALFDEX ™ used to date, together with embodiments of the present invention, will now be described with reference to the accompanying drawings, in which:

Figure 1 shows a cross-sectional perspective view of the closest analogue of the centrifugal separator ALFDEX ™;

FIG. 2 is a side cross-sectional view of a separator shown in FIG. 1 in combination with a turbine housing;

figure 3 shows in cross section a perspective view of the inlet / outlet pipe for use with the separator shown in figure 1;

FIG. 4 is a side cross-sectional view of a mold for the inlet / outlet pipe shown in FIG. 3;

figure 5 shows a perspective view of the rotor of the separator shown in figure 1;

figure 6 shows in cross section a perspective view of the rotor shown in figure 5;

Fig.7 shows a perspective view from the end face of the rotor shown in Fig.5, in which the upper rotor disk is shown removed from the rotating shaft of the specified rotor so that the rotating shaft is shown in cross section;

FIG. 8 is a cross-sectional side view of the separator shown in FIG. 1, in which the paths for the flows of separated gas and oil are illustrated;

Figures 9 and 10 are cross-sectional side views of the separator shown in Figure 1, which respectively illustrate a desired path for oil flow and an undesired path for oil flow;

figure 11 shows a perspective top view of the liner in the casing of the separator shown in figure 1;

on Fig shows a perspective side view of the liner in the casing shown in Fig.11, in which part of the outer skirt of the liner of the casing is removed so as to more clearly show an undesirable path for the flow of separated oil droplets;

on Fig shows a perspective side view of the first separator according to the present invention, in which the cage of the separator is shown in cross section so as to illustrate the rotor assembly and the liner of the casing placed inside the specified casing;

on Fig shows on an enlarged scale the plot circled by line A shown in Fig;

FIG. 15 is a cross-sectional perspective view of a first embodiment of the present invention, as shown in FIG. 13;

on Fig shows in cross section a side view of the inlet pipe connected to the inlet in the first embodiment;

on Fig shows a perspective view of the inlet pipe and the entrance of Fig. 16, separated from each other;

Fig. 18 is a cross-sectional perspective view from above of the first embodiment of Fig. 13, in which the transverse section is made through a plane parallel to the carrier plate of the first embodiment and passing through line 18-18 shown in Fig. 15;

Fig. 19 is a cross-sectional perspective view of a second embodiment in which the second embodiment is different from the first embodiment in that a plastic coating is provided at the upper end of the rotor assembly;

FIG. 20 is a cross-sectional perspective view of a first embodiment shown in FIG. 13;

on Fig shows a perspective top view of the upper rotor disk and the rotating shaft of the first embodiment shown in Fig;

FIG. 22 is a flow rate diagram showing the velocity of the incoming fluid relative to a guide surface placed on the upper rotor disk shown in FIG. 21;

on Fig shows a perspective view from below of the upper rotor disk and the rotating shaft shown in Fig;

on Fig shows a perspective bottom view of one of the many separator disks intended for placement with the possibility of sliding on a rotating shaft shown in Fig.21 and 23;

on Fig shows a perspective bottom view of a separator disk, located with the possibility of sliding on a rotating shaft shown in Fig.21 and 23;

on Fig shows a perspective view of the fan disk and the associated end plate located above the liner of the casing, which, in turn, is placed on the carrier plate of the first embodiment shown in Fig;

FIG. 27 shows a perspective side view of a plurality of separator disks disposed on a rotating shaft of FIGS. 21 and 23, wherein said disks and shaft are assembled with the components shown in FIG. 26;

on Fig shows a perspective view of the liner of the casing of the first embodiment shown in Fig.13, and the liner of the casing is shown isolated from other components, excluding protection against splashes of oil placed under the liner;

in Fig.29 shows a partial perspective bottom view of the first embodiment shown in Fig.13, showing, in particular, the turbine wheel assembly of the specified embodiment;

FIG. 30 is a partial cross-sectional perspective view of a side of the turbine wheel assembly of FIG. 29;

FIG. 31 is a partial cross-sectional perspective view of a side of a turbine wheel assembly alternative to that shown in FIGS. 29 and 30;

on Fig shows a perspective bottom view of the node of the turbine wheel shown in Fig;

FIG. 33 is a cross-sectional view of a first embodiment shown in FIG. 13;

Fig. 34 is an enlarged cross-sectional side view of the first embodiment shown in Fig. 13, which shows the flow paths of gas and separated oil droplets through a separator;

on Fig shows in cross section a view of the layout of the drive from the electric motor relative to what is shown in the above figures, where the layout of the drive from the electric motor is shown used with the existing separator of figure 1;

on Fig shows a schematic view showing the block nature of the separator system shown in Fig;

on Fig and 38 show views of the upper bearing assembly according to the first embodiment, mounted on the clamping device for friction welding;

on Fig shows a perspective side view of the upper bearing assembly mounted on the clamping device for friction welding with Fig and 38;

on Fig shows a perspective view of the node shown in Fig, placed inside the rotor casing according to the first embodiment before friction welding of the upper bearing assembly with the inner part of the specified casing; and

on Fig shows a perspective view of the upper bearing assembly attached to the inner surface of the casing shown in Fig, through the steps of friction welding.

Next, the closest analogue will be described - the ALFDEX ™ separator with reference to figures 1-12 of the accompanying drawings, with particular attention being paid to those aspects of this separator used so far that have been improved by the inventors.

A number of views of the closest analogue of the ALFDEX ™ separator assembly 2 is shown in FIGS. 1, 2, 8, 9, and 10 in the accompanying drawings. Specialists in the art should understand that the separator 2 used to date contains a generally cylindrical rotor casing 4 designed to accommodate a number of internal components that are used to separate the oil from the purged gas directed into the specified rotor casing 4.

One end of the cylindrical casing 4 is provided with a vertical annular protrusion 6, which restricts the fluid inlet 8 to the separator 2. Therefore, it should be understood that the gas discharged from the casing and requiring oil removal from it enters the separator 2 through the fluid inlet 8 .

The hole 10 in the cylindrical wall of the rotor casing 4 forms a purified gas outlet for passage from the inside of the rotor casing 4 into another casing 12 connected to the valve assembly 14 (see FIG. 1). The valve assembly 14 comprises a valve device for controlling the flow of purified gas from the separator 2. Details of the operation of the valve assembly 14 will not be described here. However, as will be apparent from FIG. 1, the outer side of the rotor housing 4 is specially designed to interface with the valve housing 12 node 14 so that the two casings 4, 12 are combined to limit the internal space between these casings 4, 12, suitable for accommodating the internal components of the valve assembly 14. Two casings 4, 12 are attached to each other by conventional by screw fasteners 16. Therefore, it should be understood that a certain casing of the valve assembly 12 can only be used together with a specific rotor of the casing 4 having the necessary mating features.

As shown in FIG. 1, the casing 12 of the valve assembly 14 is provided with a vertical annular protrusion 18 that limits the fluid outlet through which the cleaned gas is discharged from the separator 2. The annular protrusion 18 placed on the casing of the valve assembly 12 is substantially identical to the annular protrusion 6, placed on the casing 4 of the rotor. Due to their similarity, the protrusions of the inlet and outlet 6, 18 can interchangeably receive inlet / outlet nozzles having the same interface profile. In the cross section in figure 3 shows one such pipe 22, bent at an angle of 90 °. One end of the pipe 22 is provided with an annular collar 24 defining an annular recess 26. The annular recess 26 has a profile with an edge without bevel and a diameter that allows it to receive an annular protrusion of the casing 6, 18 (which also has an edge without bevel) adjacent to it.

The section surface of the protrusion 6 of the casing 4 of the rotor with the inlet pipe 28 can be seen in figure 2 of the attached drawings. It is understood that the pipe 28 shown in FIG. 2 has a bend at a different angle than the pipe 22 in FIG. 3.

The inlet / outlet nozzles are attached to the respective casings 4, 12 by fixing them on the protrusions of the casing 6, 18 using an annular washer 30, which is pressed against the protrusion 24 of the pipe 22, 28, when the threaded fasteners 32 engage with the thread of the two protrusions with thread 34. Two protrusions 34 are vertically placed on the respective housings 4, 12 and placed on either side of the annular protrusions 6, 18. The annular seal 36 is placed, held and clamped between the recess 26 and the protrusion of the casing 6, 18 so as to prevent unwanted Leaking fluid from the interface between the inlet / outlet pipe and the corresponding casing (see FIG. 2 in relation to the inlet pipe).

With another reference to the nozzles 22, 28, shown in FIGS. 3 and 2, respectively, the second end of the nozzle (remote from the end provided with a profile of the interface) is provided with teeth or serrations 38 on its outer surface, designed to capture the hose, which when used is placed at the far end of the pipe.

The fluid paths are formed by two nozzles 22, 28, each of which contains a bend having an internal angle of 40, essentially no radius of curvature. In the separator 2 used so far, the corner pipes are manufactured using injection molding (for plastic pipes) and chill castings (for aluminum pipes). As can be easily understood from figure 4 (which shows the molding of the pipe 22), in order to allow removal of the first and second molding segments 42, 44 in the directions indicated by the first and second arrows 46, 48, respectively, there is a possibility in the molding segments 42 , 44 give the radius of curvature to the inner corner 40.

Said internal components housed in the rotor housing 4 will now be described in more detail with particular attention to FIG.

First, the upper bearing assembly 50 is attached to the inner surface of the rotor housing 4 immediately after being discharged for the fluid 8. The upper bearing assembly 50 comprises bearings in a cup 52 trapped between the upper steel cap member 54 and the lower bearing housing 56 from plastic. Bearing assembly 50 is made by forming a lower bearing housing 56 around an upper steel cap element with bearings in a cup 52 securely secured therebetween. The placement of the upper bearing assembly 50 is most clearly shown in FIG. 8, although it is also shown in FIGS. 2 and 9 in the context of the existing cage 2.

Bearing socket element 56 has a circular shape and a protruding downward cylindrical wall 58 (covering the lower part of the cap element 54) which in the separator assembly 2 is adjacent to the side to the cylindrical wall of the rotor casing 4. Adhering to the cylindrical wall 60 helps to ensure proper lateral positioning of the upper bearing assembly 50 relative to the rotor housing 4. The second cylindrical wall 62 of the rotor housing 4 is placed radially inside the first cylindrical wall 60 so as to ensure correct axial positioning of the upper bearing assembly 50 relative to the rotor housing 4. The upper bearing assembly 50 is attached to the rotor casing 4 by means of three threaded fasteners (not shown). The arrangement of the separator 2 is such that the rotating axis of the upper bearing assembly 50 coincides with the central axis 64 of the rotor housing 4.

Three partially circular grooves 66 (only two of which are shown in Fig. 8) are placed in the upper bearing assembly 50 so as to allow the passage of the inlet fluid flow (as shown by arrow 68). The upper cap 54 deflects the inlet fluid from the bearings in the cup 52, however, as one of ordinary skill in the art would recognize, the lower side of the uppermost portion of the cap 54 also deflects (into the bearings in the cup 52) a lubricating oil mist that travels use up through the rotor shaft and into the upper bearing assembly 50.

The remaining internal components of the separator 2 are collected separately for the casing 4 of the rotor and then placed inside the casing 4 in the form of a single unit. A single unit contains the first group of components, which, when using the separator 2, remains stationary relative to the casing 4 of the rotor, and the second group of components, which, when using the separator 2, rotates around the central axis 64 relative to both the casing 4 of the rotor (and the casing of the valve assembly 12), and the first group components.

The first group of components contains a circular supporting plate 70 and a cup-shaped element 72, known as a casing liner. The casing liner 72 in combination with the carrier plate 70 serves to separate the separated oil from the purified gas before the separated oil and purified gas exit the rotor casing 4. The carrier plate 70 is made of steel, and the shell liner 72 is made of plastic. The carrier plate 70 and the casing liner 72 are fastened together by three fasteners with a thread 74 (only one of which is shown in FIG. 1 of the accompanying drawings), which are screwed into the protrusions 76, protruding downward from the lower side of the casing liner 72. This first group of components will be discussed in more detail later in this description.

The second group of components forms a rotor assembly and contains a rotating shaft 78, an upper rotor disk 80, several separate separator disks 82, which together form a package 84 of separator disks 82, an end plate 86, and a combined fan-turbine unit 88. The components of this second group are attached to one to another in such a way as to prevent their rotation relative to each other. The second group of components, however, is rotatably mounted relative to the first group of components by means of the lower bearing assembly 90 (see, in particular, FIG. 10).

Next, the rotor assembly formed by the second group of components will be described in more detail.

The rotary shaft 78 is made of metal material and has an annular cross section so as to form a longitudinally extending passage 92 for the flow of fluid along its entire length. When using separator 2, this flow passage 92 allows oil mist to be moved upward from the turbine casing through the rotary shaft and into the upper bearing assembly 50 so as to lubricate the bearings of said assembly 50. The limiting element 93 is in the form of an annular disk (with a cylindrical wall rising vertically from its radially outer circumferential edge), is placed on the upwardly facing inner protrusion of the indicated path for fluid flow 92 at the upper end of the rotary shaft 78. The restriction element 93 serves to reduce I the area of the path for flow through the rotating shaft 78 (thus forming a nozzle) at the exit of the rotating shaft 78 to the upper bearing assembly 50.

The outer side of the rotary shaft 78 is provided with a series of recesses and protrusions for receiving spring rings, which help to keep the components on the rotary shaft 78 in the correct axial position. One such spring ring 94 is clearly shown in FIG. 6 as forming an upwardly facing protrusion to which the washer 95 abuts. A compression spring 96 abuts the upwardly facing protrusion of the washer 95. The circular recess in which the spring ring 94 is placed has a sufficient width (t ie the dimensions of the recess in the axial direction) in order to allow the spring ring 94 to move axially along the rotating shaft 78 (inside the recess). This allows the spring 96 to apply axial force to the lower bearing assembly 90.

Other recesses are placed on the outer surfaces of the rotating shaft 78 to place and hold components on the specified shaft 78.

Each of the upper rotor disc 80, the separator discs 82 and the end plate 86 is in the form of a truncated cone (bounding the upper surface of the truncated cone 102) with a plurality of spokes such as spokes extending radially inward to the sleeve element, which is placed on the rotary shaft 78 during use.

While elements such as spokes of the upper rotor disk 89 and separator discs 82 have open spaces between them to allow fluid flow between them axially along the rotary shaft 78, elements such as spokes of the end plate 86 are interconnected on their lower surfaces so as to prevent axial fluid flow along rotary shaft 78 either up past end plate 86 or down past end plate 86.

The shape of the truncated cone of the upper rotor disk 80 and the end plate 86 is substantially identical to the shape of the separator disks 82 so as to allow the upper rotor disk 80 and the end plate 86 to be stacked with the separator disks 82, the upper rotor disk 80 being placed on top of the separator disk 84 , and the end plate 86 is placed below the package of separator disks 84. In addition, while a person skilled in the art understands that the separator disks 82 are relatively thin so as to allow place a large number of discs in a relatively short stack 84, and the upper rotor disc 80 and the end plate 86 are significantly thicker than the separator discs 82, so as to provide rigidity at either end of the disc packs 84 and thus ensure that the compressive axial force is uniformly applied to the truncated cone-shaped parts of the separator discs with the upper disc 80 and the end plate 86. The compressive force, in particular, is created by a cylindrical compression spring 86, which presses the end plate bushing 98 from bottom to top 86 slime.

Regarding the compression of the pack of disks 84 between the upper disc 80 and the end plate 86, one of ordinary skill in the art will recognize that the adjacent separator discs 82 in the stack 84 must remain separated from each other in order to allow the flow of fluid through the separator 2. These gaps between the separator discs 82 is provided by a plurality of ribs 100 (known as embossing) placed on the upper surface of the truncated cone-shaped part of each separator disc 82. Each embossing 100 comes from ialno inner edge 104 of said top surface 102 to the radially outer edge 106 of said surface. The coinage 100 protrudes on the indicated upper surface 102 and in the assembled package 84 of separator disks 82, abut against the lower side of the disk adjacent to the top. As is clear to a person skilled in the art, each separator disk 82 can be placed on the rotating shaft 78 in one of only six possible angular positions relative to the rotating shaft 78, and the placement of the coinage 100 on the indicated upper surface 102 is such that the coinage of the adjacent disc 82 should be combined one on the other hand, when the discs 82 are located in any of these six positions. As a result, the compression force applied to the disc pack 84 by the end plate 86 is transmitted through the pack 84 by the aligned coinage 100 without overlapping the gaps between the adjacent separator discs 82.

Further, with respect to the compressive force applied to the separator disc stack 84, one skilled in the art will appreciate that this force is generated by the compression spring 96 and applied to the end plate bushing 98. Due to the stiffness of the end plate 86, the compressive force is transmitted from the sleeve 98 to the truncated cone-shaped portion 108 of the end plate 86 through a plurality of radially extending spokes 110 of the end plate 86. The compressive force is then transmitted to the disc pack 84 through the truncated cone-shaped portion 108 and transmitted up through the package 84 (through coinage 100) to the truncated cone-shaped portion 112 of the upper rotor disc 80. The compressive force is transmitted from the truncated cone-shaped portion 112 to the hub 114 of the upper rotor disc 80 through six radially extending spokes 116. The compressive force can be transmitted from the truncated cone-shaped part 112 to the sleeve 114 due to the stiffness of the upper rotor disk 80. Axial upward movement of the upper rotor disk 80 along the rotary shaft 78 is prevented by compressing the upper sleeve rotor disk 114 into a circular recess 118 in the outer surface of the rotating shaft 78 (see in particular FIG. 6). Friction between the sleeve 114 and the outer surface of the rotating shaft 78 prevents the relative rotation between them.

In particular, in FIGS. 6 and 8, it can be seen that the sleeve of the upper rotor disk 80 extends axially downward along the rotary shaft 78 to a point located directly above the sleeve of the end plate 98. More specifically, the sleeve 114 extends to the entire depth of the package of separator disks 84 and separates thus, the sleeve 120 of each separator disk 82 from the rotating shaft 78 (see Fig.7). The sleeve 120 of each separator disk 82 has a hexagonal shape defining a hexagonal hole through which the rotating shaft 78 and the sleeve of the upper rotor disk 114 pass. The rotational movement of the sleeve of the separator disk 120 relative to the sleeve of the upper rotor disk 114 (and therefore relative to the rotary shaft 78) is prevented using six slots 122 placed axially along the length of the sleeve of the upper rotor disk 114 and extending axially to the six corners of the hexagonal hole bounded by the separator sleeve of the second disk 120. This arrangement of the slots 122 prevents lateral and rotational movement of the sleeve of the separator disk 120 relative to the rotational shaft 78.

A separator disk sleeve 120 of each separator disk 82 is connected to a truncated cone-shaped portion 124 of each separator disk 82 by means of radially extending spokes 126. The spokes 126 (and in reality the remainder of the corresponding separator disk 82) are made of relatively thin and resiliently flexible plastic. However, the spokes 126, however, are able to resist the deformation of the lateral and rotational forces to which they are subjected without deformation. One skilled in the art will appreciate that the compressive force produced by the compression coil spring 96 is transmitted through the separator disc package 84 by means of embossments 100 rather than by the spokes of the separator disk 126.

One of ordinary skill in the art will also appreciate that the relative geometric shape of the splines 122 and the hexagonal sleeve 120 of each separator disk 82 ensures that, as mentioned above, each separator disk 82 can fit on the rotating shaft 78 in one of only six angular positions. However, the polar or angular positions of the minting 100 of the separator discs 82 are the same regardless of which of the six angular positions is used and, accordingly, it is not possible to assemble the package of separator discs 84 on a rotating shaft 78 with the offset minting 100 of the adjacent separator discs 82.

For clarity, some figures of the accompanying drawings show a package of disks with a reduced number of available separator disks. With respect to the specific separator 2 of FIG. 1, 2, 8, 9, and 10 are simplified in this way.

As shown in FIG. 5, a second circular recess 128 is positioned on the upper end of the rotary shaft 78 in place above the first recess 118. The second recess 128 accommodates a second compression coil spring 130. The position of the second recess is such that in the separator 2 used so far, the assembly the lower end of the second spring 130 is separated from the sleeve 114 of the upper rotor disk 80 (see FIG. 6) and its axial downward movement along the rotary shaft 78 is prevented by the upwardly facing protrusion formed by the second recess 128. In addition, in the cage assembly there are 2 bearing cups in from Akane 52 adjacent the second spring 130 and compresses it downward (at an upper end of the rotating shaft 78 remaining separated from the cap member upper bearing assembly 50 cm., particularly, Figure 8). The second spring 130 applies a load to the upper bearing assembly 50 and thus reduces vibration and the associated wear of the upper bearing assembly 50.

All components of the second group of internal components, with the exception of the combined fan-turbine unit 88, are shown assembled in FIG. 6 of the attached drawings. Before installing the fan-turbine unit 88 on the lower end of the rotary shaft 78, the lower end of the shaft 78 is placed in a central circular hole made in the carrier plate 70 and the liner of the casing 72 of the first group of internal components. In this case, the lower end of the rotating shaft 78 also passes through the lower bearing assembly 90, which is fixed in the central hole of the carrier plate 70 (see, in particular, Figs. 8 and 10).

The combined fan and turbine unit 88 is attached to the lower end of the rotary shaft 78, which protrudes downward from the lower side of the carrier plate 70. The fan-turbine unit 88 is held in position at the lower end of the rotary shaft 78 by the second spring ring 132 (is held in the third circular recess on the shaft 78) and the second washer 133 adjacent to the upwardly facing surface of the second spring ring 132. Axial positioning of the fan-turbine unit 88 on the rotating shaft 88 defined by the second spring ring 132, leads to the fact that the upper surface of the block 88 is closely pressed against the reflective washer 139, which is closely pressed against the lower bearing assembly 90. In the assembled cage 2, the inner track of the lower bearing link 90 abuts against the first spring ring 94 and presses this spring ring 94 upwards, counteracts displacement under the influence of the first compression spring 96. The pressing of the inner track, the deflecting washers 139 and the fan-turbine unit 88 to the second spring ring is such that it allows you to hold these ele cients in a fixed rotational position relative to the rotary shaft 78.

The rotor assembly of the separator 2 is rotated in the direction indicated by arrow 134 (see FIG. 1) using an active hydraulic turbine. The fan-turbine unit 88 comprises a Pelton wheel 136 having a plurality of buckets 138 uniformly distributed around its circumference. When using the separator 2, a stream of oil is directed from a nozzle (not shown) inside the turbine housing 178 in the direction of the circumference of the Pelton wheel 136. More specifically, the stream is directed tangentially to a circle passing through a plurality of buckets 138, so that the stream enters the bucket aligned with its surface . The jet passes along the indicated surface, following the internal profile of the bucket, and then is diverted by the specified profile to pass along the further surface and then released from the bucket. As a result, the jet rotates the wheel 136.

A fan having a plurality of blades 140 also forms a unit with the wheel 136. The blades 140 are placed on the wheel near the underside of the carrier plate 70. The plurality of blades of the fan 140 are also in approximately the same axial position along the rotary shaft 78 as the lower bearing assembly 90 The fan blades 140 extend radially outward from the adjacent lower bearing assembly 90. Those skilled in the art will appreciate that the blade 140 rotates about a central axis 64 as the turbine wheel rotates 136. In this case, the blades of the turbine 140 efficiently discharge fluid from the area between the wheel 136 and the lower side of the carrier plate 70, thereby reducing the pressure of the fluid in the region of the lower bearing and moving the separated oil from the place above the carrier plate 70 down through the lower bearing assembly and into the casing of the turbine 178 under the carrier plate 70.

To facilitate the manufacture of the wheel 136 is made of upper and lower parts 142, 144, which are closely pressed against each other on line 146, as shown in Fig. 8 from the accompanying drawings.

As for the first group of internal components, the carrier plate 70 is made of steel and has a circular shape with a diameter substantially equal to the diameter of the rotor casing 4. The relative geometric shape is such that it allows the carrier plate 70 to be placed on the downward facing protrusion 148 at the lower end of the rotor housing 4. Thus, the lower open end of the rotor housing 4 is closed by the carrier plate 70. The carrier plate 70 is provided with a central circular hole, which in the separator assembly 2 is concentric with the rotor housing 4. In other words, in the separator assembly 2, the circular central hole of the carrier plate 70 is centered on the central axis 64 of the rotor housing 4. In addition, as is particularly clear from FIG. 1 of the accompanying drawings, the lower bearing assembly 90 is inserted into the center hole of the carrier plate 70. The radially outermost part of the lower bearing assembly 90 is fixed relative to the carrier plate 70. The radially innermost part of the lower bearing assembly 90 is placed next to the rotating shaft 78, but is not fixed on it.

As mentioned above, the first group of internal components also contains a liner of the casing 72, which is firmly fixed to the carrier plate 70. The liner of the casing 72 serves to separate the purified gas from the oil that has been separated from it, and to obtain the outlet 150 for the purified gas connected to the outlet 10 of the casing 4 of the rotor (see, in particular, figure 1). The liner of the casing 72 is represented by a single molding of plastic. However, when describing the liner of the casing 72 below, the liner will be considered as containing four parts: part of the outer cylindrical wall / skirt 152; gutter 154; a truncated cone shaped portion 156; and an outlet portion 158 restricting the release of said liner 150.

The cylindrical skirt part 152 of the casing liner 52 has the outermost diameter, which is essentially equal to the diameter of the part of the inner wall of the rotor casing 4, to which the skirt part 152 abuts. A circular recess 159 (see Fig. 12) is provided on the outer surface of the skirt part 152 for placement therein an annular seal 160, which in the separator assembly 2 provides a fluid seal between the casing liner 72 and the rotating casing 4.

The lower end of the cylindrical skirt 152 abuts against the upper side of the carrier plate 70 and is provided with a circular recess 162 (see FIG. 12) for receiving a second O-ring seal 164. It is understood that the second O-ring seal 164 provides fluid sealing between the casing liner 72 and carrier plate 70.

The second cylindrical wall is placed radially inside the outer skirt part 152 and is concentric with it, connecting at its lower end with the skirt part 152 to form a groove 154. The groove 154 together with the outer skirt part 162 forms a groove (or groove) 166 that runs along the inner cylindrical wall of the casing 4 of the rotor. The trough 166 has a U-shaped cross section and, when using a separator 2, collects separated oil droplets that are discharged from the separator disks 82 and flow down into the inner part of the rotor casing 4 under the influence of gravity (and under the influence of a gas flow moving down a spiral, as mentioned in more detail here). The trough 154 is provided with four drain holes 168 (see, in particular, FIG. 11) through which the oil collected in the trough 166 can drain so as to pass into the region closed when using the separator 2 on the underside of the casing liner 72 and c the upper side of the carrier plate 76.

The third part 156 of the casing liner 72 is in the form of a truncated cone and suspended from the groove 154. The part in the form of a truncated cone 156 is provided with a central circular hole, which in the separator assembly 2 has a central axis coinciding with the central axis 64 of the rotor casing 4. An elongated recess 170 (see FIG. 11) is placed on the upper surface of the truncated cone-shaped part 156. The recess 170 delimits a fluid passage for the purified gas, which is connected to the outlet portion 158 of the casing liner 72. A fluid passage provided the recess 170, begins at its upper end with a decrease 172 from the upper surface of the truncated cone-shaped part 156. The side walls 174, 176 of the recess 170 become higher in the direction of flow, when the passage for the fluid passes outward from the center of the liner skin xa 72. As will be apparent from the top view of the casing liner 72 shown in FIG. 11, the recess 170 forms a direct fluid passage having a length approximately equal to half the diameter of the casing liner 73.

The outlet portion 158 of the casing liner 72 is provided in the form of a generally cylindrical pipe that extends through a groove 166 between the openings in the outer skirt portion 152 and the groove 154.

A view of the separator 2 attached to the casing of the turbine 178 is shown in FIG. 2. The separator 2 is attached to the casing of the turbine 178 with three threaded fasteners 180, each of which through one of three protrusions forming one with the lower end of the casing 4 of the rotor. In FIG. 2, a side view in cross section shows only one fastener 180 and a protrusion 182. Those skilled in the art can understand from FIG. 2 that the carrier plate 70 (and therefore all components from the first and second groups) is held in the required position relative to the rotor casing 4 due to the turbine casing 178 closely pressed against the carrier plate 70 by means of the downward protrusion 148 while the rotor casing 4 and the turbine casing 178 are connected to each other. The carrier plate 70 is essentially sandwiched between the rotor casing 4 and the turbine housing 178 using threaded fasteners 180. When the threaded fasteners 180 are tightened and the carrier plate 70 is in close contact with the protrusion 148, the second compression coil spring 130 is compressed by the upper bearing assembly 50.

During operation of the separator 2, a nozzle (not shown) in the casing of the turbine 178 directs a stream of oil to the turbine wheel 136 so as to rotate the turbine wheel in the direction indicated by arrow 134, as described previously in relation to figure 1. This rotation of the turbine wheel drives the rotor assembly as a whole in the direction of arrow 134 around the central axis 64 of the rotor housing 4. In other words, the rotating shaft 78; upper rotor disc 89; a package of 84 separator discs 82; the end plate 86 and the combined fan-turbine unit 88 (i.e. collectively referred to herein as the rotor assembly) rotate together as a single assembly within the rotor housing 4 and relative to said housing and the carrier plate 70; casing liner 72; and the casing of the turbine 178.

Gas purged from the crankcase and requiring treatment in the separator 2 is introduced into the separator 2 through the fluid inlet 8, placed at the top of the rotor casing 4. As shown by arrow 68 in FIG. 8, the inlet gas enters the rotor casing 4 in a direction parallel to and in line with the central axis 64, and passes through three slots 66 in the upper bearing assembly 50 until six spokes 116 of the upper rotor disk pass by 80. The rotational movement of the six spokes also leads to lateral movement of the fluid placed between these spokes while the specified fluid moves tangentially from the circular path of the spokes 116 and is effectively released outward in the direction of the cylindrical wall ki casing 4 of the rotor. In essence, six spokes 116 give a cylindrical movement to the incoming gas.

When the intake gas flows downward through the spokes 116, 126 of the upper rotor disk 80 and the separator disks 82, the gas is displaced to the side in the direction of the cylindrical wall of the rotor casing 4 through the gaps between adjacent separator disks 82, as shown by arrows 184 in Fig. 8. The coinage 100 together with the frictional forces applied to the separator discs 82 impart a lateral motion to the fluid contained in the disc pack 84, which causes said fluid to move outward in the direction of the cylindrical wall of the rotor casing 4. This fluid movement caused by the rotation of the disk stack 84 is the main mechanism by which the fluid is drawn into the separator 2.

One of skill in the art will appreciate that oil droplets 186 tend to collect together and form larger droplets around the perimeter of the disk pack 84. In this regard, capillary forces acting on smaller oil droplets (due to the small gaps between adjacent separator disks 82) tend to prevent the dropping of small droplets from the package of disks 84. However, when more oil passes through the separator disk, smaller droplets gather together around the perimeter and form larger ones fire of sufficient weight (and corresponding "centrifugal" force) to overcome the capillary force. The oil is then released onto the cylindrical wall of the casing 4 of the rotor. After falling onto the specified cylindrical wall, oil droplets 186 tend to flow down due to gravity and gas flow through the separator 2 into the annular groove 166. The outer most circular edge of the separator package 84 is sufficiently separated from the cylindrical wall of the rotor casing 4 so as to allow to drip oil droplets without interference from the separator discs 82 down into the specified groove 166. The sealing ring 160 allows droplets to drip into the groove 166 instead of falling between the liners of the casing 72 and the casing 4 mouth ra with the possible consequence of pollution in the form of pure gas flowing from the release liner 150 housing 72 (as will be best understood by reference to Figure 1).

The oil droplets 186 collected in the trough 166 are discharged through four drain holes 168. This pressure drain is facilitated by the pressure gradients of the fluid inside the rotor housing 4 and turbine housing 178. In particular, it will be understood by those skilled in the art that due to the rotational motion of the rotary The fluid pressure in the rotor casing 4 is higher at the peripheral edge of the separator disc package 84 than in the region between the lower side of the casing liner 72 and the upper side of the carrier plate 70. As a result, a tendency I have a purified gas flow down through drain holes 168. This fluid stream tends to push the separated oil droplets along the annular groove 166 and down through the drain holes 168 onto the base plate 70 below. This gas flow is indicated by arrow 188 (see, in particular, FIG. 8). The gas flow moves radially inward through the upper surface of the carrier plate 70 towards the central circular hole in the liner of the casing 72. This flow through the carrier plate 70 tends to push the separated oil droplets through the carrier plate 70 towards the lower bearing assembly 90 through which the droplets pass oils. The blades of the rotary fan 140 of the combined fan and turbine unit 88 tend to decrease the static pressure in the casing of the turbine 178 in the region of the lower bearing assembly 90. In turn, this contributes to the absorption of oil droplets through the lower bearing assembly 90. However, the main means by which the oil drops are sucked through the lower bearing assembly 90, is provided with a reflective washer 139, which, when used, rotates with the turbine unit relative to the carrier plate 70 and pumps ASO from the rotor housing 4, even if the pressure in the turbine casing ahead of the rotor casing. The fan blades 140 then drop these droplets outward into the turbine housing 178, from where they can be returned to the engine crankcase. At the same time, the gaseous medium flowing through the carrier plate 70 is drawn upward through the central opening of the casing liner 78 and leaves the rotor casing 4 through the casing liner outlet 150 and the rotor casing outlet 10.

With reference to the accompanying drawings, it can also be understood that, along with flowing through drain holes 168, part of the purified gas flows to outlets 150, 10 along an alternative path between end plate 86 and upper part of trough 154 (without getting into trough 166). This alternative path is indicated by arrow 190.

It should be understood that the flow of oil through the lower bearing assembly 90 provides a favorable lubricating effect for the bearing assembly. The upper bearing assembly 50 is likewise lubricated by oil mist, which naturally occurs in the casing of the turbine 178 and which moves upward toward the upper bearing assembly 50 along a longitudinal flow passage 92 passing through the rotary shaft 78.

Although the separator 2 used so far has proven its operational efficiency, there are a number of problems associated with the separator that address the improvements found in the modified separators described below. These problems can be divided into three broad categories.

Firstly, the paths for the fluid through the separator 2 lead to an increase in pressure loss, which negatively affects the throughput of the separator and, accordingly, the size of the engine with which the separator can be used. The first category of problems associated with the existing ALFDEX ™ separator can therefore be considered as related to pressure loss in the fluid path.

Secondly, the layout of the existing separator is such that, under certain conditions, the purified gas may become contaminated before leaving the separator. Accordingly, the second category of problems associated with the existing separator can be considered as related to undesirable contamination of the purified gas with oil.

Thirdly, some manufacturing techniques and design features associated with an existing separator can cause assembly difficulties and / or reliability problems. In this case, the third category of problems associated with the existing separator can be considered as related to the manufacture and reliability of the separator.

Each of these categories will now be discussed in more detail.

As for the paths for the fluid flow through the separator 2, there are a number of places where relatively large pressure losses are experienced. Firstly, the internal bend angle 40 in the inlet / outlet nozzles 22, 28 is so sharp that it causes the fluid to separate from the inner surface of the nozzle in the area immediately after said internal angle 40. This separation manifests itself in recirculation of the fluid flow (or turbulence), which in turn leads to loss of energy or pressure. However, as described above with respect to FIG. 4 in the accompanying drawings, imparting a large radius of curvature to the inner corner is problematic in the manufacture of the inlet / outlet nozzle by injection molding or chill casting. As a result, the existing separator 2 experiences pressure losses in the nozzles both at the inlet to the rotor casing 4 and at the outlet of the valve assembly 12.

The inventors have also identified six spokes 116 of the upper rotor disc 80 as an additional cause of undesired pressure loss. In particular, in FIGS. 5 and 6, it can be seen in particular that each of the spokes 116 has a rectangular cross-section that represents the sharp upper edge of the vanishing for the incoming axial flow of exhaust gas while the rotor disk 80 rotates in the direction shown by the arrow 134 (see figure 5). It has been found that the shape of the spokes 116 and, in particular, the sharp edge of the flange 192 on each spoke cause increased fluid separation and undesired pressure loss.

The inventors have also found that a particular configuration of the casing liner 72 causes an increase in undesired pressure loss. In particular, during use of the separator 2, the purified gas flows down the truncated cone-shaped portion 156 of the casing liner 72 in a rotational movement about the central axis 64, as indicated by arrow 194 in FIG. 12. This purified gas stream flows along a truncated cone-shaped portion 156 after flowing down a spiral along the inner surface of the cylindrical side wall of the rotor housing 4. Therefore, it should be understood that the purified gas enters the region between the truncated cone-shaped portion 156 and above the end plate 86 from all points along the circumferential perimeter of the casing liner 72 (rather than arriving at the indicated region from one particular place). The flow path through the truncated cone-shaped portion 156 is therefore in the form of a swirl that can cause an increase in undesired pressure or energy losses. Further, the step 172 and the walls 174, 176 in the recess 170, placed in a truncated cone-shaped part 156 form additional sections of the fluid separation and the associated undesirable pressure loss.

As for the second category of problems related to oil pollution, the inventors have identified a number of signs of the existing separator 2, which increase the likelihood of contamination of purified air under certain conditions. Firstly, as mentioned earlier, the stream of purified gas directed downward through the casing 4 of the rotor partially enters the groove 166 and seeks to draw the separated oil droplets into the drain holes 168. If the flow rate of purified air is not high enough to work at a certain level of oil pollution, drops the oils collected in the trough 166 can rise onto the trough portion 154 of the casing liner 72 and then drain onto the truncated cone-shaped portion 156 of the casing liner 72 (see FIG. 10). As soon as the oil droplets fall into the region between the truncated cone shaped part 156 and the end plate 86, the oil droplets inevitably leave the separator 2, polluting the purified gas. Raising the oil droplets from the trough 166 may be the result of a low consumption of purified gas, which allows an undesirably large amount of oil to collect in the trough 166. The presence of purified gas circulating towards the top in the trough 166 can also cause the oil droplets to be sucked up and to the truncated cone-shaped portion 156 of the casing liner 72. However, a significant feature of the existing separator 2, which allows the oil droplets to rise upward from the trough 166, is the tubular outlet part 158 (see Fig. 12). Although drain holes 168 are located on either side of the outlet portion 158, it can be understood from FIG. 12 that oil droplets in the groove 166 move in a circle along the bottom of the groove 166, and if the droplets do not leak through the drain hole 168 located immediately in front of the outlet 158, oil droplets will tend to follow the path indicated by arrow 196 (see FIG. 12) and flow upstream of the outlet portion 158 and into the truncated cone-shaped portion 156 of the casing liner 72.

The inventors also found that the separated oil droplets can flow upward through the central opening of the casing liner 72 and onto the truncated cone-shaped portion 156, thereby polluting the purified gas. This undesired flow of separated oil tends to occur at a relatively high flow rate of purified gas through drain holes 168 and up through the central hole of the casing liner 72 (as indicated by the arrow in FIG. 8). Those skilled in the art should understand that a high flow rate of purified gas leads to the transfer of separated oil droplets upward through the central opening of the casing liner 72, instead of draining the separated oil droplets downward through the lower bearing assembly 90 under the influence of gravity and reflective washer 139.

The inventors also found that excess oil can be introduced into the disc pack 84 in the separator along a longitudinal path for flow 92 through rotary shaft 78, as indicated by arrow 198 shown in FIG. 2. During normal operating conditions, a stream of oil, which drives the turbine wheel 136 into rotation, strikes the specified wheel and forms a mist of small droplets of oil. This mist is transported upward to the upper bearing assembly 50 and then downward through the separator disc pack 82. Typically, the amount of oil transferred in this way is sufficient to lubricate the upper bearing assembly 50, being then easily separated from the incoming gas stream by the separator disc pack 84. However, when in certain circumstances, the amount of oil transported on the rotary shaft 78 can be so large that it leads to the flow of oil from the groove 116 or to another flow to the truncated cone-shaped insertion part 156 breathing the casing 72 and then into the outlet of the purified gas 10. This may occur while, for example, the separator 2 is tilted and the lower end of the rotating shaft 78 is directly exposed to the surface of the oil reservoir located in the casing of the turbine 178.

As for the third category of problems related to difficulties in manufacturing and reliability, the inventors identified the following issues associated with the existing separator 2.

First, with respect to the manufacture of the separator 2, the inventors have found that the use of fasteners with thread 32 for attaching the inlet / outlet to the rotor housing 4 and valve housing 12 can be time consuming and require an O-ring 36.

The time required for manufacturing the existing cage 2 is also adversely affected by the need for axial alignment of the upper bearing assembly 50 with the lower bearing assembly 90 so that both bearing assemblies 50, 90 can rotate around one axis 64. In particular, the rotor casing 4 is made made of plastic using an injection molding process, and the inventors found a tendency to deform the rotor casing 4 during cooling. As a result of this deformation, the position of the first cylindrical wall 60 of the rotor housing 4 (which locates laterally the upper bearing assembly 50) tends to be in a different lateral position relative to the lower end of the rotor housing 4 than was assumed. As a result, the carrier plate 79 (and, accordingly, the lower bearing assembly 90) may be biased away from the intended position. This problem can be solved by allowing cooling of the casing 4 of the rotor for a relatively long period after the injection molding process. This long cooling period reduces the deformation of the rotor casing 4, but increases the manufacturing time.

Another problem associated with the assembly of the separator 2 relates to the interface between the various components, such as between the rotor casing 4 and the valve assembly casing 12. In particular, if the separator 2 should be provided with a different valve assembly 14 than originally provided ( or do not contain a valve assembly at all), another rotor casing 4 must also be used to ensure the proper interface with the new valve assembly (or another pipe system in which the valve assembly is not used). This can lead to an unacceptable increase in costs and manufacturing time. In addition, the asymmetry of the rotor casing 4 (caused by the shaped profile provided on the specified casing 4 for interfacing with the casing of the valve assembly 12) tends to deform the specified casing 4 during manufacture and this in turn leads to problems during assembly (for example, issues related to lack of component compatibility).

The inventors also found that the large O-ring 160 placed on the liner of the casing 72 may be damaged. In particular, an annular seal is required to seal two mating surfaces of large diameter, with one surface being placed on the casing liner 72 and one surface being placed on the cylindrical wall of the rotor casing 4. Both the rotor shroud 4 and the shroud liner 72 have relatively large manufacturing tolerances, which may result in insufficiently accurate sealing of the two components by the O-ring 160. Further, since the two components are made of plastic using the injection molding technique, each molding (and in particular the molding of the rotor housing 4) is deformed after the injection molding process. This may then cause the O-ring 160 to not properly seal the two components 4, 72. It is understood that if the O-ring 160 is damaged, the separated oil will flow into the region 200 between the outer cylindrical skirt portion 152 of the casing liner 72 and the cylindrical wall of the casing 4 rotors. Oil flowing into this region 200 will ultimately pass into the outlet 150 of the casing liner 72 and contaminate the purified gas. If the O-ring 160 is damaged in the area of the outlet 150, the separated oil will tend to leak through the O-ring 160 and directly into the outlet 150. This sealing problem can increase the production time if: (i) an action is taken to reduce the deformation effect (by increasing cooling duration after the injection molding process), or (ii) leaking components are replaced after testing the product.

In addition, the burr from the molding, located in the recess 159, in which the O-ring 160 is placed, can damage the O-ring.

The inventors also identified the reliability issue associated with the layout for accommodating the separator discs 82 with a fixed angular orientation relative to the rotating shaft 78. As explained above with respect to FIG. 7 from the accompanying drawings, the rotation of the separator discs 82 relative to the rotating shaft 78 is prevented by six spokes ( mounted on a rotating shaft 78) interacting with a hexagonal hole in the sleeve 120 or each separator disk 82. However, the vibration to which the separator is usually subjected during use (such as engine vibration) can cause wear on the interface between the slots 122 and the hexagonal hole in the sleeve 120. This wear can lead to significant relative rotational movement between the separator discs 82 and the rotating shafts 78. In fact, the inventors found that adjacent the separator discs 82 can be rotated relative to each other to such an extent that the coins 100 are not aligned, allowing you to close the space between adjacent separator discs 82. E whether this happens with a significant number of discs 82, the depth of the package of separator discs 84 may decrease to such an extent that the sleeve 98 of the end plate 86 is pressed by the compression spring 96 to the sleeve of the upper rotor disk 114. It is clear that the end plate 86 can no longer transmit compressive force to the package of separator disks 84 and, as a result, individual separator disks 82 will be able to freely move axially up and down along the rotating shaft 78 (the same as turning relative to the rotating shaft 78). This movement is highly undesirable and significantly reduces the separator capabilities of the package of separator disks 84.

Another reliability issue identified by the inventors relates to fretting on the interface between: (i) the rotating shaft 78 and the upper or lower bearing assemblies 50, 90; and (ii) a rotating shaft 78 and a first compression spring 96. Those skilled in the art will appreciate that fretting corrosion occurs when relative movement between the components is possible (for example, due to the relatively loose combination of these components). The rotating shaft 78 passes through the upper and lower bearing units 50, 90 and the first compression spring 96 with a relatively loose fit. This allows axial preloading of the first and second compression springs 96, 130 to be applied to the upper and lower bearing assembly 50, 90. In particular, based on the drawings, it is understood that the first compression spring 96 exerts axial force on the lower bearing assembly 90, and the second the compression spring 130 applies axial force to the upper bearing assembly 130. The loose fit of the rotating shaft 78 with the upper and lower bearing assemblies 50, 90 and the first compression spring 96 allows vibration between the components. This, in turn, enhances fretting corrosion on these components. Relative movement between the components can also allow solids to enter between the particles, which can further accelerate wear and lead to reliability problems.

Improved separators developed by the inventors to solve these problems will now be described with reference to FIGS. 13-41.

Those skilled in the art will immediately recognize from the accompanying drawings that the advanced separators developed by the inventors have many components that are similar or identical to the closest analogue, separator 2, with respect to the functions that they perform and their basic configuration. Such components will be described later in the context of improved separators using the same reference numerals as used above with respect to existing separator 2. For example, from what is shown in FIG. 13 of the accompanying drawings, one skilled in the art will recognize that improved separator 2 ′ shown in this figure, it contains a generally cylindrical rotor casing 4 ', which corresponds to the rotor casing 4 of the existing separator 2 and performs a similar function. The structural and functional differences between such respective components will be apparent to those skilled in the relevant drawings, however, they will be discussed in detail with significant differences in the problems to be solved, providing improvements in the existing separator 2 or in the manufacturing process of the existing separator 2.

Those skilled in the art will understand that the improved separator 2 ′ comprises a generally cylindrical rotor shroud 4 ′ and a number of internal components that serve to separate the oil from the purge gas directed to said rotor shroud 4 ′. As described below, some of the internal components are placed inside the rotor case 4 ', while other internal components (for example, a combined fan-turbine unit) are placed outside the rotor case 4', but nevertheless are placed in another case (for example, the case turbines).

The upper end of the cylindrical casing 4 'is provided with a vertical annular protrusion 6', which limits the fluid inlet 8 'to the improved separator 2'. Gas purged from the crankcase and requiring the removal of oil from it enters the separator 2 'through the inlet 8' for the fluid.

A hole 10 'in the cylindrical wall 201 of the rotor casing 4' forms an outlet through which the cleaned gas passes through the inside of the rotor casing 4 'into a separate casing 12' of the valve assembly 14 '(see, in particular, FIGS. 13, 14 and 15) . The outlet 10 'passes through the cylindrical protrusion 202, being surrounded by it, and the protrusion departs from the outer surface of the casing 4' of the rotor.

The valve assembly 14 'comprises a valve device for controlling the flow of purified gas from the separator 2'. Regarding the above description of the existing separator 2, the details of the operation of the valve assembly 14 'are not described here. One skilled in the art, however, will be familiar with the functional action of a valve assembly intended for use with an advanced separator.

As should be apparent from FIGS. 13 and 14, and in particular from FIG. 15, the internal components of the valve assembly 14 ′ are completely enclosed in the housing 12 ′ separated from the rotor housing 4 ′. In particular, the casing of the valve assembly 12 ′ comprises first and second parts 203, 205 that mate with one another to form a closed, sealed space in which the internal components of the valve assembly 14 ′ are housed. On Fig it can be seen that the upper end of the first part 203 of the casing of the valve assembly 12 'is provided with a protrusion 207 through which a conventional threaded fastener 16' is passed for screwing to another protrusion 209 on the rotor casing 4 '.

On Fig it can also be seen that the lower end of the first part 203 of the casing of the valve assembly 12 'is provided with a generally cylindrical part 211 that extends from the casing of the dripped assembly 12' and into the rotor casing 4 'through the outlet 10' of the rotor casing 4 '. The O-ring 213 is placed on the outer surface of the cylindrical part 211 and is adjacent to the protrusion (described on the indicated surface), which faces the inner part of the rotor casing 4 'in the separator assembly 2'. The protrusion thus prevents an undesired displacement of the annular seal 213 along the cylindrical part 211 when said part 211 is pushed through the outlet during assembly and the annular seal 213 interacts with said opening 10 '. In particular, the annular seal 213 hermetically interacts with the inner cylindrical surface of the protrusion 202 surrounding the outlet 10 '.

While the O-ring 213 is placed closer to the root end of the cylindrical part 211 (i.e., the end of the cylindrical part adjacent to the rest of the casing of the valve assembly), the second O-ring 215 is placed on the outer surface of the free end of the cylindrical part 211 (remote from the root end). As with the first O-ring 213, the second O-ring 215 abuts the protrusion facing the inside of the rotor casing 4 'so as to prevent unwanted movement of the second O-ring 215 when said seal is pressed into the end use position in the separator assembly 2' . In particular, in FIG. 15, it will be understood that in the separator assembly 2 ′, the second O-ring 215 is hermetically engaged with the outlet 150 ′ of the casing liner 72 ′.

One of ordinary skill in the art will understand that the first O-ring 213 prevents leakage of purified gas and / or oil droplets between the rotor housing 4 'and the valve housing 12' and from undesirable leakage from the separator 2 'into the environment. One skilled in the art will also understand that the second O-ring 215 prevents oil droplets from seeping into the outlet 150 'of the casing liner 72' and contaminating thus the purified gas leaving the rotor casing 4 'through the cylindrical part 211. The small outer diameter of the cylindrical part 211 and the first and second O-rings 213, 215 (compared with the large diameter of O-rings 160 in the existing separator 2) allows the use of relatively small manufacturing tolerances, which ensures a low failure rate in two O-rings 213, 215. In this regard, it will be clear, for example, that the degree of deformation of the cylindrical part of the relatively small diameter 211 will be less than that of the rotor casing 4 of the existing relatively large diameter separator 2.

The lower end of the first casing part 203 of the valve assembly 12 'is provided with a second protrusion 207 placed on one side of the cylindrical part 211. As with the first protrusion 207 placed on the upper end of the first part 203, the second protrusion 207 on the lower end of the first part 203 accepts the usual a threaded fastener 16 'for threaded connection with a second protrusion 209 placed on the lower end of the rotor casing 4' (see Fig. 18 with respect to these second protrusions 207, 209).

As a result of the fact that the casing of the valve assembly 12 'is a separate casing from the casing 4' of the rotor and is geometrically independent of it (other than for pairing the cylindrical part 211 with the outlet 10 'and joining the upper and lower pairs of protrusions 207, 209), the casing 4 'of the rotor of the improved separator 2' has a generally more cylindrical shape than the rotor of the casing 4 of the existing separator 2. In this regard, it is noted that the existing casing 4 of the rotor contains on its one side a relatively complex and three-dimensional shaped profile, which the fifth serves to form part of the existing casing of the valve assembly 12 (instead of a simple interface surface with it). However, in FIG. 15, it can be seen that the rotor casing 4 ′ of the improved separator 2 ′ does not contain the complex and three-dimensional shaped profile mentioned above.

Due to the fact that the rotor casing 4 'has a cylindrical shape, the casing 4' can be made using injection molding technique with a reduced degree of deformation during the cooling process compared to the casing 4 of the existing separator 2. This allows easier axial alignment upper and lower bearing assemblies 50 ', 90'. In addition, it is understood that the rotor casing 4 'shown in the accompanying drawings may be connected by alternative valve assemblies to the valve assembly 14' shown in the accompanying drawings, wherein the alternative valve assemblies have a cylindrical portion 211 suitable for mating with the outlet 10 ' rotor housing 4 'and protrusions 207 suitable for mating with the protrusions 209 of rotor housing 4' (as is the case with the valve assembly 12 'shown in FIG. 15). For example, if the alternative valve assembly has a casing with a cylindrical part and two protrusions identical to the cylindrical part 211 and the protrusions 207 shown in FIG. 15, and with the same relative placement as shown in FIG. 15, the alternative casing may be significantly larger than the casing of the valve assembly 12 ′ shown in FIG. 15 and to accommodate a completely different valve arrangement compared to the valve assembly 14 ′ shown in the accompanying drawings. This allows the block design of the separator 2 'with increased uniformity of parts between the various layouts of the separator.

On Fig it can be seen that the casing 12 'of the valve assembly 14' is provided with a vertical annular protrusion 18 ', which limits the outlet for the fluid through which the purified gas passes from the separator 2'. The annular protrusion 18 'placed on the casing of the annular assembly 12' is essentially identical to the annular protrusion 6 'placed on the casing 4' of the rotor. Due to their similarity, the inlet and outlet protrusions 6, 18 can interchangeably accept inlet or outlet nozzles having the same interface profile. Identical inlet or outlet nozzles 22 'having a 90 ° bend are shown in FIG. 13. The inlet pipe 22 'is shown in cross section mating with the protrusion 6' of the rotor casing 4 'and is also shown separated from said protrusion 6' in FIG.

As will be most clearly seen in a cross-sectional side view of FIG. 16, the interior space 216 of the nozzle 22 ′ is combined with the curved surface of the protrusion 6 ′ to limit the path for the fluid to flow with a bend of 90 ° and, importantly, with a radius of curvature on the outside and inside corners. As a result, the tendency for the fluid to separate from the internal bend angle is significantly reduced compared with the case of the fluid flowing through the acute angle 40 with the existing arrangement. In turn, pressure losses are also reduced.

The interface between the inlet or outlet nozzles 22 'and the corresponding protrusions of the casing 6', 18 'will now be described in more detail with reference to the protrusion of the casing of the rotor 6' (which is identical to the protrusion 6 'of the casing of the valve assembly 12').

As shown in FIGS. 16 and 17, the vertical protrusion 6 ′ of the rotor casing 4 ′ is provided with an annular protrusion having a generally cylindrical wall 217 centered on a longitudinal axis coinciding with the central axis 64 ′ of the rotor casing 4 ′. The free end of the cylindrical wall 217 (remote from the rest of the rotor casing 4 ') is provided with a circular edge 219, forming a curved surface 221, protruding inwardly into the hole formed by the protrusion 6'. In cross section (see FIG. 16), curved surface 221 has a partially rounded shape and passes through an arc 223 approximately 110 ° long. The partially rounded surface 221 is oriented so that the radial part 225 of the indicated surface 221 runs parallel to the longitudinal axis of the cylindrical wall 217. With the specific arrangement shown in FIG. 16, the arc 223 through which the partially rounded surface 221 unfolds ends on the said radial part 225. It can also be understood from the cross-sectional view of FIG. 16 that the outer cylindrical surface 227 of the protrusion 6 ′ coincides with said radial portion 225 and intersects with a partially rounded surface 221 for 229 forming the upper edge protrusion 6 '.

And again, as shown, in particular, in FIG. 16, when the nozzle 22 'is considered to be provided with a profile for mating with the protrusion 6', so that the inner surface 216 of the nozzle 22 'is combined with the partially rounded surface 221 of the protrusion 6' to obtain a smooth surface free from ribs, up or down protrusions, tears and / or any other signs that cause pressure loss. In particular, the geometric shape of the nozzle 22 'is such that the transition from the inner surface 216 of the nozzle 22' to the partially rounded surface 221 of the protrusion 6 'does not form a fluid flow along the combined surface (in any direction through the nozzle 22') with an obstacle or other sign, creating pressure loss. Given the symmetry of the protrusion 6 'this remains true regardless of the angular or polar positioning of the pipe 22' relative to the casing 4 '.

A smooth transition between the inner surface of the nozzle 22 'and the partially rounded surface 221 is achieved by arranging the improved separator 2' by configuring the inner surface of the nozzle 22 'so that at every point where the inner surface of the nozzle 216 converges with the partially rounded surface 221, the inner surface of the nozzle 216 oriented tangentially to a partially rounded surface 221. Accordingly, with respect to the internal bend angle formed by the combination of the nozzle with the protrusion, the inner the surface of the nozzle 216 converges with the partially rounded surface 221 on said edge 229 of the protrusion 6 'and at this meeting point is oriented perpendicular to the said radial part 225 (i.e., tangent to the partially rounded surface 221). The point at which the inner surface of the nozzle 216 converges with the partially rounded surface 221 of the protrusion 6 ', sequentially moves radially inward along the partially rounded surface 221 when it moves around the circumference around the protrusion 6' to the outer corner of the bend formed by the combination of the nozzle and the protrusion. The inner surface 216 can be seen in FIG. 16 converging with the partially rounded surface 221 at the edge 231 of the inner surface of the pipe 216.

In practice, due to the restrictions imposed by the injection molding technique and the cost restrictions associated with large tolerances, the transition between the partially rounded surface 221 and the inner surface of the nozzle 216 will not necessarily be completely free from tears and other signs that cause pressure loss. In particular, a gap is possible between the edge 231 of the pipe 22 'and the partially rounded surface 221 of the protrusion 6'. This gap can be reduced in practice by fabricating one or both of the nozzle 22 ′ and the partially rounded surface 221 of steel (or another metal material) using a casting technique.

The nozzle 22 'is also provided with a generally cylindrical protrusion in the form of a cylindrical wall 223 having an inner and outer diameter equal to the diameter of the cylindrical wall 217 of the protrusion of the casing 6'. The cylindrical wall 233 of the pipe 22 'concentrically mates with the cylindrical wall 217 of the protrusion of the casing 6' while the pipe 22 'is placed on the specified protrusion 6'. Curved wall 235 extends radially outward from said edge 231 of the inner surface of the nozzle to the upper edge of the cylindrical wall 233. In cross section, it is partially rounded in shape and configured as concentric with the protrusion surface 221 of the casing 6 ′ adjacent to it.

Two ribs 237 are placed on the outside of the nozzle 22 'and extend from the curved wall 235 so as to give added wall 235 additional rigidity and to prevent or reduce the deflection of the nozzle 22' between the specified wall 235 and the rest of the nozzle 22 '(see Fig.13) .

As in the case of the existing separator 2, the nozzle 22 'of the advanced separator 2' is manufactured using conventional injection molding or chill casting, resulting in a sharp internal angle 239 (see Fig. 34). This angle 239 can be considered similar to the inner corner 40 of the existing pipe 22. However, it is understood that the presence of a partially rounded surface 221 of the protrusion of the casing 6 'in combination with the improved pipe 22' provides imparting a radius of curvature to the interior of the bend in the flow path in the casing 4 '. As mentioned above, this does not depend on the angular orientation of the nozzle 22 'relative to the casing 4'. The separation of the fluid from the inner surface of the bend is thereby significantly reduced or avoided, and the pressure reduction in this part of the flow path is likewise reduced or avoided.

And finally, in relation to the geometric shape of the nozzle 22 ', the second end of the specified nozzle (remote from the end having the profile of the interface at placement) is provided with teeth or notches 38' on its outer surface to capture the hose, which during use is placed over the second end branch pipe.

It is emphasized again that the protrusion 6 ′ of the rotor casing is identical to the protrusion 18 ′ of the casing of the valve assembly 12 ′ and that the inlet pipe 22 ′ is connected to this second protrusion of the casing 18 ′ in the same manner as described above with respect to the protrusion of the rotor casing 6 ′.

From the shown it should be clear that the pipe 22 'can rotate freely, being worn or being adjacent to the protrusion 6', as shown in Fig.16. Thus, the pipe 22 'can be friction-welded to the protrusion 6' so as to firmly attach the pipe 22 'to the casing with the required angular orientation. Specialists in the art should understand that this method of attaching the nozzle 22 'does not require the use of threaded fasteners, as the existing separator 2. It is also clear that this method of friction welding allows you to attach the nozzle 22' at any angular orientation relative to the casing 4 'and provides sealing around the entire circumference (or closed loop) without the need for an annular seal. In particular, the heat generated by the frictional forces acting between the adjacent surfaces of the casing 4 '(i.e., the protrusion 6') and the pipe 22 'during relative rotation of these surfaces causes the melting of these surfaces. Then the rotation is stopped and the indicated surfaces harden, thus fastening one to the other.

While said friction welding is an effective way of bonding the material of the nozzle 22 'with the material of the casing 4', other methods of bonding these materials can be used (for example, adhesive bonding, ultrasonic welding or vibration welding).

Said internal components will now be described in more detail with reference to FIG. 34.

First, the upper bearing assembly 50 ′ is attached to the inner surface of the rotor casing 4 ′ immediately after the fluid inlet 8 ′. The upper bearing assembly 50 'is identical to the upper bearing assembly 50 of the existing cage 2 and as such comprises bearings in a cup 52' sandwiched between the upper steel cap element 54 'and the lower bearing housing 56' of plastic. The upper bearing assembly 50 '(and also the lower bearing assembly 90') comprise roller bearings (like the existing cage 2), but may also comprise plain bearings or friction bearings instead.

In particular, the bearing housing element 56 'has a circular shape and a downwardly projecting cylindrical wall 58' (accommodating the lower part of the cap element 54 '), which in the separator 2' is assembled inside (but not touching) the cylindrical wall 60 'of the casing 4 'rotor. The cylindrical wall 60 'extends downward from the upper inner surface of the rotor casing 4'. The circular rib 238 also extends downward from the upper inner surface of the rotor casing 4 'and is placed radially inside the first cylindrical wall 60'. The cylindrical wall 60 ', the circular rib 238 and said protrusion 6' of the rotor casing 4 'are concentric with one another and are centered on the central axis 64' of the rotor casing 4 '.

As will be described in more detail below (with reference to FIGS. 37 and 41), the upper bearing assembly 50 ′ is attached to the upper inner surface of the rotor housing 4 ′ by friction welding technique. In particular, the lower bearing housing 56 'is welded to the rib 238. Threaded fasteners are not used to fasten the upper bearing assembly 50' to the rotor housing 4 ', as is done in the existing cage 2. The arrangement is such that the rotating axis of the upper bearing assembly 50 'coincides with the central axis 64' of the casing 4 'of the rotor.

Three partially rounded slots 66 'are placed on the upper bearing assembly 50' (only two of which are shown in Fig. 34) so as to allow flow of fluid through them (as shown by arrows 68 '). The upper cap element 54 'deflects the incoming fluid from the bearings in the cup 52'. As in the existing cage 2, the lower side of the uppermost part of the cap element 54 'also deflects (inside the bearings in the cup 52') a lubricating oil mist that moves upstream of the rotor shaft during use.

The remaining internal components of the separator 2 'are assembled separately from the rotor casing 4' and then are placed with partial retrieval in the casing 4 'as a single unit. As in the case of the existing separator 2, this single unit can be considered as containing the first group of components, which during use remains stationary relative to the casing 4 'of the rotor, and the second group of components, which during use rotates around the central axis 64' relative to the casing 4 'rotor (and valve housing 12') and the first group of components.

The first group of components contains a circular supporting plate 70 'and a cup-shaped casing element / liner 72'. As in the existing separator 2, the casing liner 72 'and the carrier plate 70 act in combination with each other to separate the separated oil from the purified gas until the separated oil and purified gas exit the rotor casing 4'. The carrier plate 70 'is made of steel, and the casing liner 72' is made of plastic. The carrier plate 70 'and the casing liner are fastened together by three threaded fasteners 74' (see Fig. 29), which are screwed into the protrusions 76 ', protruding downward from the lower side of the casing liner 72'. The bearing plate 70 'closes the open end of the rotor housing 4' to create an enclosed interior space in the housing 4 ', in which several components from the second group are placed. In this regard, the rotor casing 4 'can be considered as the first part of the casing, limiting the internal space, designed to accommodate components for the separation of substances (for example, oil and gas) and for directing substances to various outlets from the specified internal space. The carrier plate 70 'can be considered as the second part of the casing, limiting the specified internal space together in the first part of the casing.

The first group of components will be discussed later in this description.

The second group of components forms a rotor assembly and contains a rotary shaft 78 ', an upper rotor disk 80', several separate separator disks 82 ', which together form a package 84' of separator disks 82 ', a fan disk 240 and an end element / plate 86', a guard disk from splashing 242 and a combined fan-turbine unit 88 '. The rotating shaft 78 'is made of a metal material, while the rest of the mentioned components of the second group are made of plastic and made by injection molding. The mentioned components of the second group are attached to each other in such a way as to prevent or at least limit their rotation relative to each other. Cylindrical compression springs (made of metal material) are also used in the second group of components, as will be described in more detail below. The second group of components is mounted rotatably on the first group of components using the lower bearing assembly 90 'and, in the cage assembly 2', is mounted rotatably on the motor housing 4 'by the upper bearing assembly 50'.

The rotor assembly formed by the second group of components will now be described in more detail.

The rotary shaft 78 'has an annular cross-section so as to obtain a longitudinal passage 92' for the fluid along its entire length. When using a separator 2 ′, this fluid passage 92 ′ allows oil mist to be transferred from the turbine housing through a rotating shaft to the upper bearing assembly 50 ′ so as to lubricate the bearings of said assembly 50 ′. The outer side of the rotary shaft 78 'is provided with a series of recesses and ledges, which help to keep the components in the proper axial position on the rotary shaft 78'.

Each of the upper rotor discs 80 ', the separator discs 82', the fan disc 240 and the end plate 86 is in the form of a truncated cone (describing the upper and lower surfaces in the form of a truncated cone) connected to a Central sleeve element, which during use is located near the rotating shaft 78 '.

In the case of the fan disk 240, the truncated cone-shaped part 290 is connected by the corresponding central sleeve element 292 by means of the second truncated-cone-shaped part 294. This second truncated cone-shaped part 294 is continuous in order to form a fluid barrier and thus prevent axial fluid flow along the rotary shaft 78 'either up past the fan disk 240, or down past the fan disk 240.

The truncated cone shape of the second truncated cone shaped portion 294 has a larger cone angle than other truncated cone shaped portions of the improved separator 2 ′. In other words, the opposite sides of the second truncated cone-shaped portion 294 converge or diverge more quickly than in the case of the first truncated cone-shaped portion 290 of the fan disc 240 or the truncated cone-shaped portion of the upper rotor disc 80 ′, the separator disc 82 ′ and the end plate 86 '(and in fact a truncated cone-shaped dividing lid member 268 of the casing liner 72') which all have the same cone angle. The central sleeve element 292 is a cylindrical wall mounted vertically on a second truncated cone-shaped portion 294 (see, in particular, FIGS. 26 and 33). The longitudinally extending grooves 296 (only one of which is shown in FIG. 26) are placed along the full thickness of the cylindrical wall of the fan sleeve element to accommodate a slot 254 extending radially from the rotating shaft 78 '. This prevents the rotation of the fan disk 240 relative to the rotating shaft 78 '.

The lower side of the first truncated cone-shaped portion 290 of the fan disc 240 is provided with a plurality of embossing elements 298 evenly spaced around the central axis of the fan disc 240. Each embossing element 298 is represented as a straight ridge protruding downward from the bottom side of the first truncated cone-shaped portion 290 and stretching radially from the radially innermost edge of the first truncated cone shaped portion 290 to the radially outermost edge of the first truncated cone and parts 290. In the separator assembly 2, the minting elements 298 abut against the upper surface of the truncated cone-shaped part of the end plate 86 'and thus provide a gap between the disk 240 and the end plate 86' through which fluid can pass (such as indicated by arrow 188 in FIG. 34). During use of the separator 2 ', the rotation of the embossing elements 298 imparts a rotational movement to the fluid located between the fan disk 240 and the end plate 86'. As a result, the specified fluid moves outward towards the cylindrical wall 201 of the rotating casing 4 '. Drops of oil (and / or in reality other liquid or particulate contaminants that the gas stream carries) are effectively discarded onto the cylindrical wall 201 of the rotatable casing 4 'and drain (or fall) down onto the carrier plate 70'. Gaseous fluid ejected from the space between the fan disk 240 and the end plate 86 'either flows down onto the carrier plate 70' or directly leaves the rotor casing 4 ', as will be explained in more detail below.

As for the end plate 86 ′, the radially innermost circular edge of the truncated cone-shaped portion 108 ′ is connected to the sleeve element 98 ′ by a plurality of spokes 110 ′ (see FIG. 18). However, the cylindrical wall 300 also extends downward from the indicated radially innermost edge of the truncated cone-shaped portion 108 ′. In the separator 2 'assembly, the cylindrical wall 300 is centered on the central axis 64' and extends sufficiently downward along the rotary shaft 78 'so as to pass through the central hole provided in the casing liner 72'. Although said wall 300 has a generally cylindrical shape, the inner surface 302 of said wall 300 describes the shape of a truncated cone, so that the inner diameter of the cylindrical wall 300 decreases upward in the separator assembly 2 ′. The outer cylindrical surface of the wall 300 has substantially the same diameter as the central hole of the casing liner 72 'and, in the separator 2' assembly, is placed in the specified hole with minimal clearance between the wall 300 and the casing liner 72 '. This tight fit, allowing relative rotation between the end plate 86 'and the shell liner 72', helps to reduce the amount of oil that can leak between the wall 300 and the center bore of the shell liner 72 'so as to contaminate the purified gas. In addition, the internal truncated cone-shaped surface 302 of said wall 300 serves to resist the passage of oil droplets flowing upward into the space between the fan disk 240 and the end plate 86 '. Those skilled in the art will understand that oil droplets in contact with a truncated cone-shaped surface of the wall 300 will undergo rotational movement and, due to the shape of the truncated cone of the indicated surface, acting in a downward direction.

The splash guard disk 242 includes a flat ring disk 304, which is connected via six spoke elements 306 extending radially inward, to a central sleeve element 308, which in the separator 2 'assembly is located around the rotary shaft 78' (see, in particular, FIG. 28). The diameter of the central hole bounded by the flat annular disk 304 is substantially equal to the inner diameter of the lower end of the cylindrical wall 300 of the end plate 86 '. The fluid flow passing through the splash guard disc 242 in the region between the fan disc 240 and the end plate 86 ', therefore, does not encounter a sign causing a significant loss of pressure at the interface between the splash guard 242 and the end plate 86'. It should be understood that the annular disk 304 forms a flange element extending radially from the lower end of said cylindrical wall 300 and serving to cover any gap between the outer surface of said cylindrical wall 300 and that part of the casing liner 72 'defining the central hole, through which said wall 300 passes. In this way, the flat annular disk 304 reduces the likelihood of splashing out the separated oil droplets or otherwise moving upward from the carrier plate 70 'and through the central the opening of the casing liner 72 'so as to contaminate the purified gas.

It will further become clear that the indicated region between the fan disk 240 and the end plate 86 ′ limits the path 616 for the fluid flow to pass through the inlet 618 (limited by the splash guard 242) to the outlet 620 (limited by the edges of the fan disk 240 radially outwardly perimeter and end plate 86 '), as shown in Fig. 34.

The sleeve element of the splash guard 242 is made as a cylinder with its upper end closed by a flat wall located perpendicular to the longitudinal axis of the specified cylinder (and, in the separator 2 'assembly, the central axis 64'). The inner diameter of said cylinder is larger than the outer diameter of the rotating shaft 78 'and the flat wall is provided with a central hole through which said shaft 78' passes in the separator assembly 2 '. The arrangement is such that in the separator assembly 2 ′, the rotating shaft 78 and the cylinder of the sleeve element 308 define an annular space into which a cylindrical compression spring 96 ′ is inserted, which is intended to press the splash guard 242 against the end plate 86 ′, which, in turn, presses the fan disk 240 and the disk pack 84 'to the upper rotor disk 80'.

Those of skill in the art would understand that the splash guard 242 is manufactured separately from the end plate 86 'so as to allow the cylindrical wall of the end plate 86 to fit in the center hole of the casing liner 72'. This cannot be possible if the splash guard 242 is integral with the end plate 86 ', since the annular disc 304 exceeds the diameter of the central hole in the casing liner 72'.

As noted above, the geometrical shape of the truncated cone of the upper rotor disc 80 ′, the fan disc 240 (in relation to its first truncated cone-shaped part), and the end disc 86 ′ are substantially identical to the shape of the separator discs 82 ′. This allows the upper rotor disk 80 ', the fan disk 240, and the end plate 86' to be placed in a bag with separator disks 82 ', the upper rotor disk 80' being placed on top of the separator disk 84 'and the end plate 86' being placed at the bottom of the separator disk 84 ' . A fan disk 240 is placed between the end plate 86 'and the separator disk 82' at the very bottom (i.e., at the base) of the separator disk package 84 '.

In addition, while those skilled in the art may consider the need for relatively thin separator discs 82 'such that a large number of discs can be assembled in a relatively short stack 84', the upper rotor disc 80 'and the end plate 86' are significantly thicker than separator discs 82 ', so as to provide rigidity at either end of the stack of discs 84' and thus allow uniform application of compressive force to the truncated cone-shaped parts of the separator disc 82 'by means of the upper disc 80' and the end howl plate 86 '. It should be understood that the compressive force is exerted by said cylindrical compression spring 96 ', which presses up on the lower side of the sleeve 308 of the splash guard 242. In turn, the sleeve 308 of the splash guard 242 pushes up on the lower side of the adjacent sleeve 98' of the end plate 86 '.

Regarding the compression of the pack of disks 84 'between the upper disc 80' and the end plate 86 and the end plate 86, one skilled in the art will understand that, as in the existing separator 2, the adjacent separator discs 82 'in the package 84' must remain separated one from another in order to allow the passage of fluid flow through the advanced separator 2 '. This separation of the separator discs 82 ′ is provided in the improved separator 2 ′ by a plurality of gaskets 246. Each gasket 246 is a small dot placed or protruding on the top surface 102 ′ of the truncated cone portion 124 ′ on each separator disk 82 ′ (see FIG. .twenty).

The lowest separator disk 82 'in the bag 84' can also be further separated from the fan disk 240 so as to allow fluid to flow between them. If such separation is required, suitable gaskets are required. Ideally, the upper surface of the first truncated cone-shaped portion of the fan disc 240 (which is placed below the truncated cone-shaped parts of the disc pack 84 'and connects the fan disc bushing with the second truncated cone-shaped portion of the fan disc 240) is provided with spacers 246 in the same manner as a truncated cone-shaped part of each of the separator discs 82 '.

Each of these gaskets is round in shape, although other gaskets may be used (for example, an oval shape may be used). Any alternative forms of gaskets 246 preferably have curved edges so as to reduce fluid pressure loss in the fluid flowing past the gaskets.

The first group of gaskets 246 is placed along a concentric circle together and next to the inner circular edge 104 'of the indicated upper surface 102'. Each gasket 246 in this first group is placed adjacent to that part of the inner circular edge 104 'where the spoke of the disk 82' is connected to the truncated cone-shaped part of the disk 82 '. A second group of knitting needles 246 are arranged in a circle concentric with and adjacent to the outer circumferential edge 106 'of the indicated upper surface 102'. A third group of gaskets 246 is located in a circle concentric together and approximately halfway between the inner and outer circular edges 104 ', 106' of the truncated cone-shaped part of the disk 82 '.

As will be shown in more detail below, each separator disk 82 '(and, in fact, the disk 240) can be placed on the rotating shaft 78' in one of only three possible angular positions relative to the rotating shaft 78 ', and the positioning of the gaskets 246 on the indicated upper surface 102 'is such that the gaskets 246 of the adjacent discs 82' should be aligned with each other while the discs 82 'are placed in any of these three positions. In other words, while the separator discs 82 'are axially advanced on the rotary shaft 78' and in contact with each other to form said package 84 ', it is inevitable that (i) each gasket 246 of a particular disk 82' is located directly above the gasket 246 of an adjacent disc 82 'located under said specific disc 82' in a package 84 ', and that (ii) each gasket 246 of a specific disc 82' is located directly below the gasket 246 of an adjacent disc 82 'located above said specific claim 82 'in the package 84'. As a result, the compressive force applied to the disk package 84 'by the end plate 86' is transmitted through the package 84 'by means of aligned gaskets 246 without bridging the gap between adjacent separator disks 82. This allows fluid residues to flow out between the separator disks.

According to the drawings, it can be understood that the gaskets 246 have small radial dimensions, as well as small circumferential dimensions compared with the dimensions (diameter) of the respective separator disks. This allows the fluid to flow relatively unhindered from the gaskets in the circumferential direction through the indicated upper surface of the disk 102 'in the same way as in the radial direction through the indicated surface 102'. This minimizes pressure loss in the fluid flow between adjacent discs 82 '.

The upper rotor disk 80 'and the rotating shaft 78' are shown in isolation from the other components of the separator 2 'in FIGS. 21 and 23 of the accompanying drawings. A sleeve 114 'of the upper rotor disk 80' is formed on the outer surface of the rotating shaft 78 'and is thus connected with the specified shaft 78'. This coupling prevents relative rotation between the sleeve 114 'and the rotating shaft 78'.

The sleeve 114 ′ of the upper rotor disk 80 ′ extends axially upward along the rotary shaft 78 ′ and terminates at the upper end of said shaft 78 ′. The upper part of the rotary shaft 78 ', around which a second compression coil spring 130' is placed, is thus provided with a plastic liner (sleeve) (preferably thermoplastic). This coating protects the spring 130 'and, in particular, the shaft 78', from fretting corrosion. The first and second groups of internal components of an alternative embodiment of the first embodiment 2 'are shown in Fig. 19. An alternative separator is the same as in the first embodiment, except that the portion of the upper end of the rotary shaft 78 'does not have a plastic lining adjacent to the second coil spring 130'.

The hub 114 'of the upper rotor disc 80' also extends axially down along the rotary shaft 78 'and ends at a point located directly above the lower bearing assembly 90'. The lower bearing assembly 90 'is in contact with the metal end of the rotating shaft 78' in the separator assembly 2 '. In particular, the sleeve 114 'extends to the full depth of the package of separator disks 84' and thus separates the sleeve 120 'of each separator disk 82' from the rotary shaft 78 '. It is also understood that the sleeve 114 'also provides the rotating shaft 78' with a lining (sleeve) of plastic (preferably thermoplastic) in the region of the first coil spring 96 '. And in this case, the lining protects the spring 96 'and, in particular, the shaft 78' from fretting corrosion.

The truncated cone-shaped portion 112 ′ of the upper rotor disc 80 ′ is connected to the sleeve 114 by twelve radially spaced spoke elements. Each spoke element 116 'has a rectangular cross-section, the upper (smaller) side 310 of which is adjacent to the radially innermost circular edge 312 of the truncated cone-shaped portion 112'. Each spoke element 116 ′ extends radially downward from said edge 312. This arrangement is such that while the upper rotor discs 80 ′ rotate during use of the separator 2 ′, each spoke element 116 ′ acts like a fan blade and imparts movement to the adjacent fluid environment. Those of skill in the art would understand that the motion imparted to the fluid by each spoke element 116 ′ results in a current flowing tangentially from the circular path of the spoke elements 116 ′ and is effectively thrown outward under the truncated cone-shaped portion 112 ′ and through the stack of disks 84 'in the direction of the cylindrical wall of the casing 4' of the rotor. The operation of the spoke elements 116 'as fan blades causes the upper rotor disk 80' to rotate, drawing the gas into the rotor housing 4 'through the fluid inlet 8' (as indicated by arrow 68 'in FIG. 34) and through the spaces 600 between the spoke elements 116' so that these gaps 600 form the entrance to the rotor assembly.

The fluid entering the rotor casing 4 ′ passes through three partially rounded slots 66 ′ in the upper bearing assembly 50 ′. The spoke elements 116 'of the upper rotor disc 80' are located in the separator 2 'assembly directly under the three partially circular slots 66'. As specifically shown in FIG. 34 from the accompanying drawings, the radial dimensions of the partially rounded slots 66 ′ are smaller than the radial dimensions (i.e. length) of the spoke elements 116 ′ with the result that a large proportion of the incoming fluid initially strikes only that segment of the spoke element 116 ', which is located immediately below the partially rounded slots 66'. This segment of each spoke member 116 ′ is provided with a curved fluid guide vane 314 extending upward from its upper side (or leading edge) 310. The purpose of each fluid guide vane 314 is to reduce or eliminate pressure losses associated with separating the inlet fluid from spoke elements 116 '. This is achieved by supplying a substantially axial flow of fluid to be introduced into the rotor housing 4 'with a guide vane having an aerodynamic cross section and cord oriented so as to have a substantially zero angle of attack with the incoming fluid flow (or other angle of attack that is not causes fluid to separate from the guide vane 314).

A cross-sectional view through a segment of a spoke member 116 ′ provided with a guide vane 314 is shown in FIG. The surface of the guide vane 314 serves to direct a fluid that approaches the leading edge 310 of the spoke member 116 ′ in the alignment direction with the spoke member 116 ′. A cord 316 associated with a leading edge 318 of the guide vane 314 is oriented substantially at a zero angle of attack to the fluid flowing above said guide vane 314. The direction of this fluid relative to the guide vane 314 is indicated by arrow 320 and, as shown in FIG. 22, should be understood as dependent on the axial velocity (i) of the fluid inlet flow (Q / A, where Q is the volumetric flow rate of the fluid through the inlet; and A is the cross-sectional area of the inlet flow path), and (ii) the tangential velocity vlyayuschey blade 314 (ω.r, where ω is the angular velocity of the upper rotary disc, and r is the radial distance of the guide blade from the rotation center). Since the fluid flow direction 320 relative to the guide vane 314 depends on the radial position r along the guide vane 314, the cord 316 can be oriented at an angle that changes with the radial position. In other words, the guide vane for the fluid 314 may be twisted so as to ensure that the guide vane 314 is correctly aligned with the incoming fluid flow in all radial positions along the guide vane 314. In particular, an acute angle 322 between the cord 316 and the vertical baseline 324 (parallel to the central axis 64 'of the separator 2' assembly) may sequentially increase from the inner most radial position in the direction of the outer most radial position along the spoke th element 116 '.

One skilled in the art will appreciate that while using the advanced separator 2 ′, the incoming air flows axially downward through three partially rounded slots 66 ′ and strikes the guide vanes 314, which are placed a short distance below the indicated slots 66 ′ and that rotate in a circular path around a central axis 64 '. Since the cord 316 of the leading edge 318 of each guide vane 314 is oriented so as to have a substantially zero angle of attack with respect to the incoming fluid stream, the fluid flows from both sides, low pressure 324 and high pressure 326 of the guide vane 314, and is directed for flow in axial direction relative to the spoke elements 116 'without separation from the guide vane 314 or the corresponding spoke elements 116'. In this way, pressure losses associated with the passage of fluid through the upper rotor disk 80 'are avoided or minimized.

Another consequence of reducing the pressure loss provided by the guide vanes 314 is that the number of spoke elements 116 'can be increased (compared to the existing separator 2) without undesired effect on the flow rate of the fluid through the separator 2' as a whole. The increased number of spoke elements 116 'allows the transmission of large compressive forces between the truncated cone-shaped portion 112' and the sleeve 114 'of the upper rotor disk 80'. An increased number of spoke elements 116 ′ may also improve the balance of the upper rotor disc 80 ′.

It should be noted that FIG. 22 is a schematic cross-sectional view of the guide vane 314 and the corresponding spoke element 116 ′, and it does not necessarily represent a particularly preferred geometric shape or, in reality, particularly preferred rotational speeds and fluid flow rates.

As for FIG. 21, a cylindrical ridge 328 will be placed concentrically radially with the innermost edge 312 of the truncated cone-shaped portion 112 ′, vertically rising from it. In the separator 2 'assembly, ridge 328 is placed radially outward from the downwardly extending cylindrical wall 58' of the upper bearing assembly 50 '. The comb 328, however, is placed adjacent to said cylindrical wall 58 in order to prevent (or significantly limit) the leakage of fluid between them (see, in particular, FIG. 34).

Three slots 254 extend radially from the sleeve 114 ′ of the upper rotor disk 80 ′, as will be most clearly seen in FIG. 23 from the accompanying drawings. The three slots 254 are separated by equal distances around the central longitudinal axis of the upper rotor disk 80 'and extend axially along the sleeve 114' (and therefore along the rotary shaft 78 ') from the lower side 330 of the spoke elements 116' to the point along the sleeve 114 ', which the separator 2 'assembly is placed approximately halfway along the central sleeve element 292 of the fan disk 240.

Each slot 254 has a base 350 and a ridge 352. The base 350 is connected to the rest of the sleeve 114 '. Crest 352 is adjacent to base 350, forming a free end on slot 254. The base 350 of each slot 254 is wider (i.e., larger in circumference) than crest 352. As a result of the difference in width between the base and crest 350, 354 on any a ledge 354 is provided from the sides of each slot 254 at the junction between the base 350 and the ridge 352. As shown in particular in FIG. 23, it can be seen that the width of the base 350 of each slot 254 increases from the lower end of each slot 254 to the upper end of each slot 254. In addition, the width of each base is 350 approx. It is equal to the width (i.e. circumferential size) of one of the twelve spokes 116 'of the upper rotor disc 80'. The ridge 352 of each slot 254 is also circumferentially aligned with and adjacent to the spoke element 116 '.

The sleeve 120 'of each separator disk 82' has an opening 252 through which the rotating shaft 78 'and the sleeve of the upper rotor disk 114' are passed (see in particular FIGS. 23, 24 and 25). The rotational movement of the sleeve of the separator disk 120 'relative to the sleeve of the upper rotor disk 114' (and therefore relative to the rotating shaft 78 ') is prevented by three splines 254 placed axially along the length of the sleeve of the upper rotor disk 114' and entering radially into the corresponding female mating profile limited by the bore 252 of the sleeve of the separator disk 120 '. This arrangement of the splines 254 prevents lateral and rotational movement of the sleeve of the separator disk 120 'relative to the rotating shaft 78'. In particular, the surfaces of the ridge 352 of each slot 254 (whose surfaces 356 extend generally radially) are adjacent to the respective surfaces 358 (which surfaces 358 also extend generally radially) of said mating profile in order to prevent relative rotation of the separator disk 82 'and the upper sleeve rotary disk 114 '(and rotary shaft 78'). It is understood that adjacent surfaces 356, 358 press each other during use in a direction generally perpendicular to each of these surfaces 356, 358, and for this reason there is little or no relative sliding movement of these surfaces 356, 358 and little or no the absence of frictional wear of these surfaces 356, 358, which can lead to increased or undesirable relative rotation between the separator disk 82 'and the sleeve of the upper rotor disk 114'.

A separator disk sleeve 120 ′ in each separator disk 82 ′ is connected to a truncated cone-shaped portion 124 ′ of each separator disk 82 ′ by twelve radially extending spoke elements 126 ′. As with the existing separator 2 ', the spokes 126' (and the rest of the corresponding separator disk 82 ') are made of relatively thin and resilient plastic. And in this case, as in the existing separator 2 ', the spokes 126' can resist the lateral and rotational forces to which they are subjected without deformation, and the compressive force created by the coil spring 96 'is transmitted through the separator disc package 84' at the intervals 246 rather than on the spokes of the separator disk 126.

One skilled in the art will also appreciate that the relative geometric shape of the slots 252 and the holes 252 of each separator disk 82 'ensures that, as mentioned above, each separator disk 82' can fit on the rotating shaft 78 'in one of only three angular positions. By positioning the gaskets 246 relative to the hole 252, the polar and angular positioning of the gaskets 246 of the separator disk 82 'remains the same relative to the rotating shaft 78' regardless of which of the three angular positions is used and, accordingly, it is not possible to assemble the package of separator disks 84 'on rotating shaft 78 'when offset relative to each other gaskets 246 adjacent separator discs 82'. However, each separator disk 82 'is provided with markers that can be aligned with the markers of other disks 82' in the disk stack 84 '. In this way, all discs 82 'in the package 84' will have the same angular position relative to the rotating shaft 78 '. The marker is represented by a ridge 256 located on the sleeve between the two spokes 126 'and radially extending a short distance to the outside.

For clarity, in FIG. 13, 15, 19, 20, 27, 33, 34 of the accompanying drawings, a stack of disks 84 'is shown with a reduced number of separator disks present.

An annular recess 258 (see FIG. 21) concentric with a rotating shaft 78 'is placed on the upper surface of the sleeve of the upper rotor disk 211'. An annular recess 258 accommodates a second compression cylindrical spring 130 'and prevents downward axial movement of this spring 130' along the rotary shaft 78 '. In addition, in the separator 2 'assembly, the bearing cup in the cup 52' abuts against the second spring 130 'and compresses it downward (with the upper end of the rotating shaft 78' remaining separated by a gap from the cap element 54 'of the upper bearing assembly 50' - see, in particular, Fig. 34).

During assembly of the advanced separator 2 ', all components except the combined fan-turbine unit 88' of the second group of internal components are mutually interconnected. The upper rotor sleeve 114 '(and the rest of the upper rotor disc 80') is injection molded with the rotating shaft 78 'in place. Then, the separator disk pack 82 'of the separator disc 82' is put on the rotating shaft 78 'from its lower end so as to be placed in contact with the lower side of the truncated cone-shaped portion 112' of the upper rotor disc 80 '.

Before installing the fan-turbine unit 88 on the lower end of the rotary shaft 78, the lower end of the shaft 78 is passed through a central circular hole placed in each of the number of the carrier plate 70 and the casing liner 72 of the first group of internal components. In this case, the lower end of the rotating shaft 78 also passes through the lower bearing assembly 90, which is attached to the central hole of the carrier plate 70 (see, in particular, Figs. 8 and 10).

Further, with respect to the compressive force exerted on the separator disc stack 84 ', one skilled in the art will appreciate that this force is generated by a compression coil spring 96'. During use of the separator 2 ′, the compression spring rotates together with the rotating shaft 78 ′, and the lower end of the compression spring 96 ′ abuts in the radially inner race of the lower bearing assembly 90 ′ so as to press against it and transmit the indicated force upward to the guard sleeve 308 from splashing out. The compressive force is then transmitted from the splash guard sleeve 308 to the end plate sleeve 98 '. The rotation of the splash guard 242 relative to the end plate 86 'collides with the resistance associated with frictional forces between the splash guard sleeve 308 and the end plate sleeve 98' (which, as is understood, depends on the compressive force).

Due to the rigidity of the end plate 86 ', a compressive force is transmitted from the sleeve 98' to the truncated cone-shaped portion 108 'of the end plate 86' through the plurality of radially extending members 110 '. The compressive force is then transmitted to the embossing elements 298 of the fan disc 240 through the truncated cone-shaped portion 108 ′ and then transmitted from the truncated cone-shaped portion 290 of the fan disc 240 upward through the stack 84 ′ (via gaskets 246) to the truncated cone-shaped part 112 ′ upper rotor disc 80 '. The compressive force is transmitted from the truncated cone-shaped part 112 'to the sleeve 114' of the upper rotor disc 80 'through twelve radially extended spokes 116' The compressive force can be transmitted from the truncated-conical part 112 'to the hub 114' due to the rigidity of the upper rotor disc 80 '. Axial upward movement of the upper rotor disk 80 'along the rotary shaft 78' in response to compressive force is prevented by placing the sleeve of the upper rotor disk 114 'in contact with the downward facing step 250 on the rotary shaft 78'. The axial movement of the sleeve of the upper rotor disk 80 'down along the rotary shaft 78' is prevented by placing the sleeve of the upper rotor disk 114 'in contact with the upwardly facing step 248 on the rotary shaft 78'.

The adjacent discs 82 'in the disc pack 84 can be further firmly connected to each other. This will increase the stiffness of the disk pack 84 'and ensure that the relative rotational positions of the adjacent disks 84' remain constant (i.e., ensures that the gaskets of the disks 246 remain aligned so as to transmit compressive force without closing the gap between adjacent disks 82 '). The disks 82 'can be fastened together by welding (for example, ultrasonic welding).

As in the existing separator 2 ', before installing the fan-turbine unit 88' on the lower end of the rotating shaft 78 ', the lower end of the shaft 78' is inserted into the circular hole provided in each element from the carrier plate 70 'and the casing liner 72' of the first group internal components. The lower end of the rotary shaft 78 'also passes through the lower bearing assembly 90', which is attached to the Central hole of the bearing plate 70 '(see, in particular, Fig.29 and 30).

The combined fan-turbine unit 88 'is attached to the lower end of the rotary shaft 78', which protrudes downward from the lower side of the carrier plate 70 '. The fan-turbine unit 88 'is held in position at the lower end of the rotary shaft 78' by means of a spring ring 132 '(held in a circular recess on the lower end of the rotary shaft 78') and a compression coil spring 360 placed around the lower end of the rotary shaft 78 'and adjacent to the upward facing surface of the snap ring 132 '.

The snap ring 132 'and compression spring 360 are placed in the cavity in the combined fan-turbine unit 88'. The spring compression 360 presses upward inside the cavity so as to shift the fan-turbine unit 88 upward in contact with the radially inner race of the lower bearing assembly 90 '. This arrangement is most clearly shown in FIG. 30 from the accompanying drawings. According to this figure, it is understood that the upwardly reflecting surface 139 ′ is provided on said block 88 ′ and is placed radially inside the fan blades 140 ′ of said block 88 ′. The reflective surface 139 'performs the same function as the reflective washer 139 in the existing separator 2, but forms an integral part with the fan-turbine unit 88' instead of being a separate adjoining component. The radially inner part of the reflective surface 139 'is pushed up to fit to the inner race of the lower bearing assembly 90', which, in turn, is pushed up to the carrier plate 70 '. The reflective surface 139 'and the radially outer race of the lower bearing assembly 90' are axially separated so that a separated oil stream is passed down through the lower bearing assembly 90 'and radially outward through the gap into the turbine housing.

The rotor assembly of the separator 2 rotates in the direction indicated by the arrow 134 '(see FIGS. 29 and 30) using an active hydraulic turbine. As in the existing separator 2 ′, the fan-turbine unit 88 ′ comprises a Pelton wheel 136 ′ having a plurality of buckets 138 ′ uniformly distributed around its circumference. When using separator 2, a stream of oil is directed from a nozzle (not shown) inside the turbine housing in the direction of the circumference of the Pelton wheel 136 '. More specifically, the jet is directed tangentially to a circle passing through the plurality of buckets 138 ′, so that the jet enters the bucket aligned with its surface. The jet passes along the indicated surface, following the internal profile of the bucket, and then is diverted by the specified profile to pass along the further surface and then released from the bucket. As a result, the jet rotates the wheel 136 '.

A fan having a plurality of blades 140 ′ also forms a unit with the wheel 136 ′. The blades 140 'are placed on the wheel next to the underside of the carrier plate 70'. The plurality of fan blades 140 ′ are also in approximately the same axial position along the rotary shaft 78 ′ as the lower bearing assembly 90 ′. Fan blades 140 extend radially outward from an adjacent lower bearing assembly 90. Those skilled in the art will appreciate that the blade 140 'rotates about a central axis 64' when the turbine wheel 136 'rotates. In this case, the blades of the turbine 140 'effectively release fluid from the area between the wheel 136' and the lower side of the carrier plate 70 ', thereby reducing the pressure of the fluid in the region of the lower bearing assembly 90', helping to remove the separated oil from the place above the carrier plate 70 'down through the lower bearing assembly and into the turbine housing under the carrier plate 70 '.

To facilitate the manufacture of the wheel 136 'is made of upper and lower parts 142', 144 ', which are closely pressed against each other on the line 146' by two threaded fasteners (only one of which is shown in Fig.30 from the attached drawings).

The plurality of fan blades 140 'and the reflective surface 139' are integrally formed with the upper part 142 'of the fan-turbine unit 88'. The lower part of the fan-turbine unit 88 'is provided with a lower flat element 364, which in the separator assembly 2' lies in a plane perpendicular to the central axis 64 'and across the downwardly facing hole in the passage 92' of the rotary shaft 78 '. The flat member 364 is nevertheless spaced apart from said opening into a flow passage 92 'so as to allow fluid to flow into said opening.

The flat element 364 is provided with four holes 366, which are located at equal distances along an imaginary circle centered on the central axis 64 'in the separator assembly 2'. One skilled in the art will appreciate that it is possible to use an alternative number of holes 366, although the holes should be positioned so as to provide rotational balancing of the fan-turbine unit 88 '.

In particular, the openings 266 are placed radially outside the opening in the flow passage 92 '. Therefore, it should be understood that the arrangement is such that mist from oil droplets can flow upward through openings 366 from the turbine housing and thus enter the cavity in the fan-turbine unit 88 'and flow upward through the passage 92' of the rotary shaft 78 '. However, it will also be appreciated that the flow from the openings 366 to said openings of the flow passage 92 is directed radially inwardly. When using the separator 2 ', the fan-turbine unit 88' rotates, of course, in the direction indicated by arrow 134 'and while relatively large oil bodies flow from the oil droplets radially inward from the openings 366 into the passage 92' flowing through the openings 366 will move laterally under the influence of a rotating flat element and tend to drop from the hole to the flow passage 92 '. For example, if the vehicle is tilted or otherwise moved in such a way that the oil splashes upward from the turbine housing through the openings 366 so as to fill the cavity of the fan-turbine 88 ', the lateral movement imparted to the oil in said cavity tends to prevent the oil from flowing in inward, in the direction of the rotating shaft 78 '. In this way, an undesired upward flow of a large amount of oil through the rotary shaft 78 'and into the disk stack 84' is avoided.

Two drain holes 368 are provided in the flat member 364 so as to allow oil to be drained from the cavity inside the fan-tube unit 88 ′ back into the turbine housing. The drain holes 368 are diametrically opposed to each other and form a slot in the flat element 364 and in a common cylindrical wall vertically extending from the circular perimeter of the indicated flat element 364. The location of the drain holes 368 in the radially outermost part of the turbine cavity ensures that the oil is thrown to the outside the perimeter of the specified cavity from the rotating shaft 78 'effectively drains from the fan-turbine unit 88'.

While the flat element 364 is shown in the embodiment of FIGS. 29 and 30 as integrally with the bottom 144 ′ of the fan-turbine unit 88 ′, in the alternative embodiment shown in FIGS. 31 and 32 of the accompanying drawings, the end the plate 364 is represented by a circular disk separated from the bottom 114 of the fan-turbine unit 88 '. As shown in FIGS. 31 and 32, the separate flat member 364 of the alternative embodiment is a circular disc provided with holes 366 in the same manner as in FIGS. 29 and 30. However, the alternative flat member 364 is fixed in position relative to the rest of the fan-turbine unit 88 'using threaded fasteners (which pass through it) in the absence of drain holes 368. In this alternative arrangement, drain holes 368 are placed exclusively in the cylindrical wall of the lower part 144', which is relies concentrically with a circular edge around the perimeter 364 and moves away from them upwards. The lower part 144 'of the fan-turbine unit 88' is also provided with a second cylindrical wall 370, which is placed in the cavity of the fan-turbine unit 88 'and extends downward to obtain a downwardly facing annular surface to which the flat element 364 can be pressed by two threaded fasteners 362 The recesses are placed in a downwardly directed annular surface so as to form a passage for fluid 372 between said cylindrical wall 370 and flat member 364. During use, oil flowing upwardly of the upper surface of plate member 364 extends toward the drain hole 368 along the path 372 to flow.

While the fan-turbine unit 88 'of FIGS. 31 and 32 is provided with an outer cylindrical wall and a flat element 364, which together delimit the cavity and are further provided with an additional cylindrical wall 370, against which the flat element 364 is placed, the fan-turbine element 88 is otherwise similar to the same unit in the existing separator 2 and is attached to the rotating shaft 78 'in the same way as on the existing separator 2. In particular, the fan-turbine unit 88' is attached to the rotating shaft 78 'with a washer 133', which pushes up on the lower part 144 'of the indicated block 88' and is held in position by a spring ring 132 placed in a circular recess on the outer surface of the rotating shaft 78 '. It should be understood that the washer 133 'and the snap ring 132 form alternative fastening means for the compression spring 360 and the snap ring 132 is shown in FIGS. 29 and 30.

As for the first group of internal components, the carrier plate 70 'has a circular shape with a diameter substantially equal to the diameter of the rotor casing 4'. As in the existing separator 2 ′, the relative geometric shape is such that it allows the carrier plate 70 ′ to be placed on the downward facing step 148 ′ at the lower end of the rotor housing 4 ′. Thus, the lower open end of the rotor casing 4 ′ is closed by the carrier plate 70 ′. However, in the improved separator 2 ′, the lower open end of the rotor casing 4 ′ abuts against the upper side of the carrier plate 70 ′ and is provided with a circular recess 260 to accommodate an annular seal 262 (see FIG. 34). It should be understood that the second O-ring seal 262 provides fluid sealing between the rotor housing 4 'and the carrier plate 70'.

In addition, in the separator 2 'assembly, the radially outermost surface of the circular edge 630 (forming the base surface) of the carrier plate 70' coincides in contact with the cylindrical inner surface 632 surrounding the lower open end of the rotor casing 4 '. Thus, the carrier plate 70 'is aligned on the sides in the desired final position relative to the casing 4' of the rotor (see Fig.13).

The carrier plate 70 'is also provided with a central circular hole, which in the separator 2' is assembled concentrically with the rotor casing 4 '. In other words, in the separator assembly 2 ′, the circular central hole of the carrier plate 70 ′ is centered on the central axis 64 ′ of the rotor housing 4 ′. In addition, as will be particularly apparent from FIG. 34 of the accompanying drawings, the lower bearing assembly 90 ′ is inserted into the center hole of the carrier plate 70 ′. The radially outermost part of the lower bearing assembly 90 ′ is fixed relative to the carrier plate 70 ′. The radially innermost part of the lower bearing assembly 90 is placed adjacent to the rotating shaft 70, but is not fixed thereto.

As mentioned above, the first group of internal components also includes a casing liner 72 ', which is firmly attached to the carrier plate 70'. As in the existing separator 2 ', the casing liner 72' serves to separate the purified gas and oil that has been separated from it. The casing liner 72 ′ of the advanced separator 2 ′ also forms a purified gas outlet 150 ′ that is hermetically connected to the cylindrical inlet portion 211 of the casing of the valve assembly 12 ′ (see FIG. 15).

The casing liner 72 'is presented as a single molding of plastic. However, in the description of the casing liner 72 'below, the liner will be considered as comprising four parts: an outer reflective wall 264 having a truncated cone shape; a supporting wall 266 having a cylindrical shape; a truncated cone-shaped dividing lid member 268; and an outlet portion 270 restricting said release of the liner 150 ′ (see, in particular, FIGS. 27 and 28).

The dividing lid member 268 of the casing liner 72 'has a truncated cone shape and is supported by a supporting wall 266. The dividing lid element 268 is provided with a central round hole, which in the separator 2' has a central axis coinciding with the central axis 64 'of the rotor casing 4'. An extended channel / recess 272 (see FIG. 28) is placed on the upper surface of the separation cover 268. The channel / recess 272 restricts the path of the purified gas fluid from the inlet 282 of the recess 272 to the outlet 270 (having a tubular shape) of the liner casing 72 '. The inlet 282 is bounded by a recessed circular portion of the upper edge around the perimeter 274 of the separation cover 268. The inlet 282 is generally diametrically opposed to the outlet of the casing liner 72 '. Said recessed portion of said edge along the perimeter 274 passes through an arc of approximately 80 °, which arc is centered on the indicated central axis of the opening of the casing liner. In alternative embodiments, the fluid path inlet may be limited to a recessed portion at said edge along a perimeter 274 that extends through another arc, such as between 45 ° and 110 °. In the separator assembly 2 ′, only a small distance separates the dividing lid member 268 from the end plate 86 ′. As a result, it is believed that most of the purified gas entering the region 606 between the dividing lid member 268 and the end plate 86 'does this through the gap between the recessed portion of said edge along the perimeter 274 and the end plate 86', with a relatively small proportion of the purified gas entering the specified area through the rest of the specified edge along the perimeter 274.

Therefore, it should be understood that the space between the entire circumferential edge 274 and the end plate 86 ′ forms an inlet 610 into the indicated region 606 between the dividing lid member 268 and the end plate 86 ′, however, since there is one longitudinal part 612 (i.e., inlet 282 into the channel / recess 272) of this inlet 610 has a greater depth 613 (i.e., a larger axial gap between the edge along the perimeter 274 and the end plate 86 ') than other extended parts of the inlet 610, a larger proportion of the purified gas entering the specified region 606, performs this h Res said extended portion 612 having a large depth 613. The depth of the remaining portions of said elongated inlet to (610) is a minimum so as to minimize fluid flow therethrough and thus also reduce to a minimum the passage of oil droplets therethrough. The depth of the remaining extended sections may be from one tenth to half from a greater depth 613, and preferably one third from the indicated greater depth.

When using the separator 2 ', the purified gas exiting the separator disc package 84' flows downward in the form of a spiral rotational movement along the inner surface of the cylindrical wall of the rotor casing 4 '. Therefore, it should be understood that the cleaned gas entering the aforementioned region 606 between the dividing lid member 268 and the end plate 86 'tends to do this in the form of a rotational movement in a spiral centered on the central axis 64' of the rotor housing 4 '. However, the gas flow entering the indicated region 606 through the inlet 282 is immediately directed to the outlet of the liner 150 ′ by the side walls 276, 278 of the extended recess 272. Such a directivity of the purified gas stream is also believed to reduce the rotational movement of the purified gas in a spiral immediately after entry of said gas into said extended recess 272 through the inlet of recess 282. In this regard, in FIG. 28, from the accompanying drawings, it can be seen that the upstream part of the extended recess 272 is bent (side walls 276, 278 of the recess 272 are thus consistent with the swirling inlet flow so as to substantially minimize the desired pressure loss while the fluid initially hits the side walls 276, 278) and sequentially straightens as the fluid moves down along the recess 272 in the direction to release the liner 150 '. It is believed that an immediate reduction in the vortex movement in most of the clean gas entering the region between the dividing lid member 268 and the end plate 86 'significantly reduces the pressure loss in the fluid flowing through this part of the separator 2' compared to the existing separator 2 described above .

It should be understood that the purified gas, which does not flow through the inlet 282, but which enters the region between the dividing lid member 268 and the end plate 86 'in other places along the perimeters of the dividing lid element 268, will tend to flow through the indicated region with a swirling motion up to entering the extended recess 272, in which the radially outer side wall 276, in particular, is believed to direct the fluid towards the outlet direction of the liner 150 'and also reduce the swirling movement of the fluid the second medium.

The cylindrical support wall 266 is concentrically arranged with the central hole of the separation cover element 268 and protrudes downward from the lower side of the separation cover element 268. The diameter of the support wall 266 is smaller than the edge diameter around the perimeter 274 of the separation cover element 268. In the separator assembly 2 ', the lower round edge is turned down 450 (see FIG. 27) of the support wall 266 abuts against the carrier plate 70 'at the junction between them. The support wall 266 thus supports the separation of the cover element 268 on the carrier plate 70 'and ensures the correct axial position of the separation of the cover element 268 relative to the carrier plate 70'. The supporting wall 266 is also provided with a plurality of cylindrical protrusions 452, each of which has a recess for screwing the fastener 74 '. In the separator assembly 2 ', each fastener 74' enters one of these protrusions 452 from below the carrier plate 70 'through an opening in the carrier plate 70'. Thus, the casing liner 72 'is firmly attached to the carrier plate 70'.

The lower downward circular edge 450 of the support wall 266 has a plurality of holes / recesses 454 placed at various places along the specified edge 450. As can be seen, in particular in FIGS. 27 and 34, the recesses 454 form the space between the support wall 266 and the carrier plate 70 'through which, during use of the separator 2' assembly, fluid may flow. In particular, when using the separator 2 ′, the separated oil flowing radially inside from the cylindrical wall of the rotor casing 4 ′ along the carrier plate 70 ′ passes through a plurality of recesses 454. The fraction of purified gas also flows radially inward through the upper surface of the carrier plate 70 ′ (which a qualified reader will understand) and this fluid also flows through a plurality of recesses 454. This flow is indicated by arrow 188 'in FIG. 34.

The outer reflective wall 264 extends downward from the edge around the perimeter 274 of the separation cover 268. The reflection wall 264 is in the form of a truncated cone diverging downward from the separation cover 268 in the direction of the carrier plate 70 'in the separator 2' assembly. The diameter of the reflective wall 264 at its upper end (and therefore the diameter of the edge around the perimeter 274 of the separation cover element 268) is essentially equal to the outer diameter of the package of separator disks 84 '. Due to the shape of the truncated cone of the reflective wall 264, the reflective wall 264 converges with the generally cylindrical wall of the rotor casing 4 'when moving downward. The cross-sectional area of the flow path between the reflective wall 264 and the rotor housing 4 'is therefore reduced in the flow direction (i.e., downward). The lower free end 608 of the reflective wall 264 is spaced apart with respect to the cylindrical wall of the rotor casing 4 'at a distance of 456 from 2 millimeters to 200 millimeters, and preferably 14 millimeters, above the carrier plate 70'. This gap between the outer reflective wall 264 and the rotor housing 4 'and the carrier plate 70' allows the separated oil (or other separated material) and purified gas (which does not enter the inlet of the first region 610) to flow downward along the cylindrical wall of the rotor housing 4 'and radially inward along the carrier plate 70 'past the reflective wall 264 (including its free end). In this case, the separated oil and purified gas flow through the second region 614 on the opposite side of the casing liner 72 'to the first region of the stream 606.

In addition, due to its shape of the truncated cone, the outer reflective wall 2643 moves downward from the cylindrical support wall 226. An outer reflective wall, a dividing lid member 268, and a cylindrical support wall 266 define a generally annular cavity 458 (see FIG. 34) with an open lower end. The arrangement is such as to reduce the likelihood of the separated oil flowing down along the rotor casing 4 ′ past the inlet 282 of the recess 272, only for the subsequent upward flow due to the recirculation of the fluid and thus entering the purified gas into the inlet 282.

In particular, while the relatively large gap between the rotor housing 4 'and the upper end of the reflective wall 264 allows easy entry of the separated oil between these elements, the relatively small gap between these elements at the lower free end of the reflective wall 264 reduces the ease with which the separated oil may splash or recycle upward between the indicated free end and the rotor housing 4 '. In addition, any recirculation of fluid near the radially outer perimeter of the carrier plate 70 ′ may lead to a tendency for the separated oil to flow into said cavity 458. For example, the separated oil may flow upward along the radially outer surface of the cylindrical support wall 266, externally along the lower side of the separation cap element 258 and then down along the radially inner surface of the reflective wall 264. At one time, oil may fall from the cavity 458 onto the carrier plate 70 'under the influence of gravity. It can be understood that this way of the recycle stream does not lead to the separated oil flowing upward so as to cause a risk of contamination of the purified gas entering the region between the separation cap member 268 and the end plate 86 '. So, when the purified gas flows past the inlet to the region 606 (i.e., the inlet into the space between the dividing lid member 268 and the end plate 86 ') in the direction of the carrier plate 70', any subsequent recirculation of the specified gas back upstream towards the specified inlet prevented from entering the recirculated gas (or the droplets of oil that it carries) into the indicated area 606 by means of a reflective wall 264 that effectively separates (i.e., separates) the recirculated gas from the specified of admission.

The outlet portion 270 of the casing liner 72 is represented by a cylindrical tubular element opening onto the upper surface of the dividing lid element 268 (and, in particular, opening into a recess 272 for receiving purified gas) and extending generally radially outward through the support wall 266 and the outer reflective wall 264. As will be particularly apparent from FIGS. 13 and 14 of the accompanying drawings, the outlet portion 270 is placed above the downwardly facing edge of the support wall 266. Accordingly, in the separator assembly 2 ′, the outlet portion 270 p is positioned above the carrier plate 70 'so that this fluid can flow under the outlet part 270. Preferably, the separated oil can flow under the outlet part 270 and does not tend, therefore, to rise along the outer surface of the outlet part 270 in the direction of the edge around the perimeter 274 of the separation cover element 268, where the separated oil can easily contaminate the clean gas flowing into the recess 272 of the casing liner 72 '. The free end of the outlet portion 270, remote from its end open into the recess 272, is provided with a support member 460 that protrudes downward from the lowermost part of the indicated free end so as to fit in the carrier plate 70 '. Thus, the free element 460 helps to maintain a minimum gap between the carrier plate 70 'and the outlet portion 270, and also allows the carrier plate 70' to provide support for the free end of the outlet portion 270.

During assembly, the separator 2 ′ is attached to the turbine housing (not shown) in the same manner as described above with respect to the existing separator 2 ′. In particular, the improved separator 2 ′ is attached to the turbine casing using four threaded fasteners (not shown), each of which is passed through four different protrusions 284, forming one with the lower end of the rotor casing 4 (see, in particular, FIG. .18 and 29).

Specialists in the art should understand that in the case of the existing separator 2, the carrier plate 70 '(and therefore all the components of the first and second groups) is held in position with respect to the rotor housing 4' by means of a turbine housing pressing the carrier plate 70 ' before contact with the downward facing step 148 'while the rotor shroud 4' and the turbine shroud are attached to each other. The carrier plate 70 'is essentially sandwiched between the rotor housing 4' and the turbine housing 178 'with threaded fasteners passing through four protrusions 284. After tightening the threaded fasteners and bringing the carrier plate 70' into contact with the shoulder 148 ', the O-ring 262 on said step 148 'is pressed into the corresponding recess 260, and the second compression cylinder spring 130' is compressed by the upper bearing assembly 50 '.

During operation of the improved separator 2 ′, a nozzle (not shown) in the turbine housing directs a stream of oil to the turbine wheel 136 ′ so as to rotate the turbine wheel in the direction indicated by arrow 134 ′ (see FIGS. 29 and 34). This rotation of the turbine wheel causes the rotation of the rotor assembly as a whole in the direction of the arrow 134 'about the central axis 64' of the rotor housing 4 '. In other words, the rotating shaft 78 '; upper rotary disc 80 '; package 84 'separator disc 82'; fan disk 240; end plate 86 '; splash guard disc 242; and the combined fan-turbine unit 88 '(i.e. collectively referred to as the rotor assembly) rotate together as a single assembly within the rotor housing 4' and relative to said housing 4 'and the carrier plate 70'; the liner of the casing 72 and the casing of the turbine.

Gas purged from the engine housing and requiring treatment on the separator 2 ′ is supplied to the separator 2 ′ through a fluid inlet 8 ′ located on top of the rotor housing 4 ′. As shown by arrow 68 ′ in FIG. 34, the inlet gas enters the rotor casing 4 ′ in a direction parallel to and in line with the central axis 64 ′ and flows through three slots 66 ′ in the upper bearing assembly 50 ′ before entering the inlet 600 of the rotor assembly past twelve spokes 116 of the upper rotor disc 80 '. The rotational movement of the twelve spokes 116 'also leads to lateral movement of the fluid located between these spokes, so that the specified fluid moves tangentially from the circular path of the spokes 116' and is effectively thrown outward in the direction of the cylindrical wall of the rotor casing 4. Essentially twelve spokes 116 'give the incoming gas a cylindrical movement.

When the incoming gas flows down through the spokes 116 ', 126' of the upper rotor disc 80 'and the separator discs 82', the gas moves sideways in the direction of the cylindrical wall of the rotor casing 4 'through the spaces 602 between the adjacent separator discs 82', as shown by arrows 184 ' in Fig.34. When flowing along this path, the direction of fluid flow changes by more than 90 °.

It should be understood that the gaps 604 between the radially outermost edges around the perimeter of the adjacent separator discs 82 'together represent an outlet from the rotor assembly.

Those skilled in the art should also understand that oil droplets 186 'tend to collect together and form larger droplets as they move through the separator discs and are discarded onto the cylindrical wall of the rotor housing 4'. After falling onto said cylindrical wall, the oil droplets 186 'tend to run down due to gravity on the carrier plate 70'. The outermost circumferential edge of the separator bag 84 'is sufficiently separated from the cylindrical wall of the rotor casing 4' so as to allow oil droplets to flow down unhindered onto said carrier plate 70 '. The O-ring 262 ensures that oil droplets cannot drain between the carrier plate 70 'and the rotor housing 4'.

Those skilled in the art should also understand that due to the rotational movement of the rotor assembly, the fluid pressure inside the rotor housing 4 'is greater at the edge around the periphery of the separator disc stack 84' and the carrier plate 70 'than in the region enclosed by the support wall 266 and the lid element 269 of the liner casing 72 'and the supporting plate 70'. As a result, there is a tendency for the purified gas to flow down along the cylindrical wall of the rotor casing 4 'and relatively inward along the carrier plate 70'. This fluid flow tends to push the separated oil droplets down along the cylindrical wall onto the carrier plate 70 below and then radially inward along the carrier plate 70 'through the openings in the support wall 266 of the casing liner 72'. This gas fluid stream is indicated by arrow 188 '(see FIG. 34). The flow of gas fluid moves radially inward through the upper surface of the carrier plate 70 'in the direction of the Central circular hole in the liner of the casing 72'. This flow through the carrier plate 70 'tends to drop separated oil droplets through the carrier plate 70 in the direction of the lower bearing assembly 90' through which these oil droplets pass. The rotating fan blades 140 'of the combined fan and turbine blocks 88' tend to decrease the static pressure in the turbine housing (to which the rotor housing 4 'is attached during use) in the region of the lower bearing assembly 90' so as to draw oil droplets through the lower bearing assembly 90 '. The fan blades 140 'then drop these droplets radially outward into the turbine housing, from where they can return to the crankcase. At the same time, gaseous fluid flowing through the carrier plate 70 ′ is pulled upward through the center bore of the casing liner 72 ′ to radially outward travel between the end plate 86 ′ and the fan disk 240. The gaseous fluid can then leave the rotor casing 4 ′ by flowing through the specified cylindrical portion 211 of the casing of the valve assembly 12 ', which is hermetically connected to the liner of the casing 72' and passes through the liner of the casing 150 'and the outlet 10' of the rotor casing.

With reference to the accompanying drawings, it should be understood that along with flowing along the upper surface of the carrier plate 70 ′ and through the holes in the support wall 266 of the casing liner 72 ′, a portion of the purified gas enters said cylindrical portion 211 along an alternative path between the lower side of the end plate 86 ′ and the upper side of the separation cover element 268 of the casing liner 72 '. This alternative path is indicated by arrow 190 '.

It should be understood that, as in the existing cage 2, the oil flow through the lower bearing assembly 90 'of the advanced cage 2' has a beneficial lubricating effect on the bearing assembly. The upper bearing assembly 50 'is likewise lubricated by oil mist, which naturally occurs in the turbine housing and which moves upward towards the upper bearing assembly 50' along an extended flow path 92 'through the rotary shaft 78'.

Any of the existing ALFDEX ™ 2 separator or advanced separator 2 'described above may include alternative means of rotating the rotary shaft 78' as shown in FIG. 35 of the accompanying drawings. As shown in FIG. 35, it can be seen that the Pelton wheel of the turbine described earlier is replaced by a brushless electric motor 380, the rotor 382 of which is attached to the lower end of the rotating shaft 78 ”under the carrier plate 70”. The electric motor 380 is shown in FIG. 35 as driving an existing ALFDEX ™ 2 separator. However, as one skilled in the art will understand, the electric motor drive system shown in FIG. 35 may also be used in connection with the improved separator 2 ′, described above.

As shown in FIG. 35, it can be seen that the electric motor 380 in the drive system with the electric motor is placed inside the housing 384, which is attached to the rotor housing 4 with a plurality of threaded fasteners 180 ′ (only one of which is shown in FIG. 35). The motor housing 384 consists of upper and lower parts 386, 388 attached to each other by suitable fastening means and with an annular seal 390 placed on the interface between them. O-ring 390 prevents unwanted penetration of dirt, water and / or other foreign material inside the casing outside the casing 384. In this way, electrical components (including printed circuits or other circuits) are isolated from materials that could cause damage and subsequent failure .

The upper part 386 of the casing 384 is provided with a downwardly projecting cylindrical wall 392 defining a central hole in said upper part 386. The cylindrical wall 392 is concentric with the rotating shaft 78 ”in the separator assembly. The reflection washer 139 'is held on the rotating shaft 78 "by a spring ring 404". The reflective washer 139 'thus extends upward through the radially inner race of the lower bearing assembly, as in the existing ALFDEX ™ 2 cage. The reflective washer 139 ”has a radially outer edge along the perimeter radially separated from the cylindrical wall 392 so as to allow passage between them polluting oil.

The upper end of another separate portion 394 of the casing of the motor 384 (having a generally truncated cone shape) is placed and sealed at the lower end of the cylindrical wall 392 of the upper part 386. The seal between the cylindrical wall 392 and the truncated cone shaped part 394 defines a closed loop and is provided with an additional ring seal 396. The lower end of the truncated cone-shaped portion 394 (having a diameter that is larger than the diameter of the upper end) is sealed relative to the lower portion 388 of the casing of the motor 384 by means of the bottom of the O-ring 398. This seal also has a closed loop shape.

Thus, on one side of the truncated cone-shaped part 394, said part 394 and the lower part 388 form a space in which the electric motor 380 is placed and into which the lower end of the rotary shaft 78 ″ enters. On the other side of the truncated cone-shaped part 394, said part 394 and the upper part 386, as well as the remainder of the lower part 388 form a fully enclosed and insulated space / compartment 406 in which electronic / electrical components (e.g., printed circuit board 408) are provided for supply of electric power and control signals to the electric motor 380. The compartment 406 is sealed not only with respect to the environment surrounding the motor casing 384, but also from the space in which the electric motor 380 is placed. Contaminant oil, which Thu through this space by using the separator does not receive at the same time access to electronic / electrical components, leading to damage.

In addition, the truncated cone-shaped portion 394 is provided with an opening (not shown) through which electric wires 410 (connecting the motor 380 and these power supply / control components) are passed, and in which these wires are sealed.

Connector 412 also extends through hole 414 into motor housing 384 so as to allow one or more electrical wires (not shown) to be placed on the outside of the separator (e.g., coupled to a vehicle that uses the separator) to connect to said power supply components / controls placed inside compartment 406. In other words, the electrical wire or wires may be provided with a plug for mechanically and electrically connecting to the connector 412. The wire or wires may transmit electricity and / or control signals for a drive system with an electric motor. Connector 412 is sealed on housing 384 so as to prevent unwanted foreign material from entering compartment 406.

While compartment 406 has a generally annular shape concentric with the rotor assembly of the separator, it should be understood that compartment 406 may have a different shape.

The stator 400 of the electric motor 380 is attached to the lower part 388 of the casing of the motor 384. The radially inner part of said truncated cone-shaped part 394, hermetically connected to the cylindrical wall 392, defines an opening having a diameter substantially equal to the inner diameter of the stator 400 of the electric motor 380.

During the use of the separator equipped with the drive system with the electric motor of FIG. 35, the electric power supply system is connected to the brushless electric motor 380 so as to drive its rotor 382 and, thus, rotate the rotary shaft 78 ”. As shown above, the separated oil flows down from the rotor housing 4 down through the lower bearing assembly 90. In a separator equipped with a drive system with an electric motor from FIG. 35, this separated oil is discharged from the lower bearing assembly into the inside of the motor casing 384 and, in particular, the space inside the cylindrical wall 392 of the upper part of the casing 386. The separated oil then passes through the rotor 380 of the electric motor 380 and leaves the casing of the motor 384 through the port 402, placed under the electric motor 380 in the lower part of the casing 388. The oil passing through the rotor 382 (silt through the space between the rotor 382 and stator 400) and coming into contact with said rotor 382 and the stator 400 does not adversely affect the operation of the electric motor 380, because the electrical stator wire 400 coated with a layer of epoxy varnish.

Further, with respect to the manufacture of the improved cage 2 ′ and, in particular, the installation of the upper bearing assembly 50 ′ on the rotor housing 4 ′, refer to FIGS. 37-41 of the accompanying drawings. These figures show the friction welding process of the upper bearing assembly 50 ′ of the rotor housing 4 ′ in the axial alignment position with the lower bearing assembly 90 ′ while the carrier plate 70 ′ is mounted adjacent to the shoulder 148 ′ at the lower end of the rotor housing 4 ′. The assembly process provides axial alignment of the upper and lower bearing assemblies 50 ', 90' despite changes in geometric shape caused by deformation of the rotor casing 4 'after injection molding of said casing 4'.

The process involves the use of a friction welding fixture 500 comprising a fixed portion 502 and a rotating portion 504 rotatably mounted on the fixed portion 502. The fixed portion 502 comprises a circular disk 506 whose diameter is equal to the diameter of the carrier plate 70 ′. The geometric shape of the circular disk 506 is such that it allows the circular disk 506 to be placed in contact with the rotor housing 4 'in the same way as the carrier plate 70' in the separator assembly 2 '(as shown in FIG. 40). The rotating portion 504 comprises a shaft 508 that extends through the center of the circular disk 506 and is oriented perpendicular to the circular disk 506. The shaft 504 is mounted relative to the circular disk 506 using a bearing assembly (not shown).

One end of the shaft 508 is provided with a head 510 to accommodate the upper bearing assembly 50 '. The head 510 is presented as a circular disk concentric with a circular disk 506 of the fixed part 502 and centered on an axis around which the rotating part 504 rotates. The diameter of the head 510 is substantially equal to the diameter of the radially inner surface of the downwardly projecting cylindrical wall 58 ′ of the upper bearing assembly 50 ′. Thus, the cylindrical wall 58 'of the upper bearing assembly 50' can be placed around the head 510 with little play between the upper bearing assembly 50 'and the shaft 508 or without it at all. The relatively rotational movement between the upper bearing assembly 50 'and the shaft 508 is prevented by protrusions 512 protruding from the round disk of the head 510. The head 510 contains three protrusions 512 that are identical to each other and evenly distributed around the axis of rotation of the shaft 508. Each of the protrusions 512 has a partially rounded shape and fits and is sized to fit in partially rounded slots 66 'of the upper bearing assembly 50'. The protrusions 512 have substantially the same size and shape as the indicated slots 66 ', and therefore the rotational movement of the upper bearing assembly 50' relative to the head 510 of the shaft 508 is essentially prevented when the protrusions 512 are inserted into the indicated slots 66 (see, in particular, FIGS. 37 and 38).

The second end of the shaft 508, remote from the end provided with a head 501, is provided with means 514 for connecting the rotating part 504 to the motor for driving the rotating part 504 into rotation with respect to the fixed part 502.

A fixture for friction welding 500 with an upper bearing assembly 50 'placed on its head 510 is shown in FIG. 39 of the accompanying drawings. With the upper bearing assembly 50 ′ placed on the head 510, the shaft 508 and the upper bearing assembly 50 ′ are inserted into the rotor housing 4 ′ as shown in FIG. 40. The circular disk 506 is placed adjacent to the lower ledge 148 'of the casing 4' of the rotor. In particular, the radially outermost surface of the circular edge 634 (forming the base surface) of the circular disc 506 is in contact with the circular inner surface 632 surrounding the lower open end of the rotor housing 4 '. In this way, the internal positioning of the upper bearing assembly 50 ′ relative to the rotor housing 4 ′ is determined. With the friction welding fixture 500 thus placed in the rotor housing 4 ', the axis of rotation of the rotating portion 504 coincides with the central axis 64' of the rotor housing 4 'described previously.

The rotating part 504 can be arranged so as to be able to move relative to the stationary part 502 in the axial direction so that the upper bearing assembly 50 ′ can move from a first position in which said bearing assembly 50 ′ is spaced apart from the upper part of the rotor housing 4 ′, in the second position, in which the bearing assembly 50 'is pressed against the ridge 238, placed on the casing 4' of the rotor (see Fig. 34). When the upper bearing assembly 50 'is mounted on the rotor casing 4', the rotor casing 4 'is held stationary and while the circular disk 506 of the fixed part 502 is adjacent to the lower ledge 148' of the rotor casing 4, the rotating part 504 rotates with a relatively large speed and moves axially further into the casing 4 'of the rotor so as to bring the rotating upper bearing assembly 50' into contact with said ridge 238. The rotating upper bearing assembly 50 'is pressed against the ridge 238 so as to generate heat of friction and thus melt adjacent surfaces of the plastics of the upper bearing assembly 50 'and the ridge 238. While the bearing assembly 50' is pressed against the ridge 238, the rotational movement of the shaft 508 is rapidly reduced and stopped so that the bearing assembly 50 'and the ridge 238 are held together when the molten plastics are cooled. The upper bearing assembly 50 'and the casing 4' of the rotor are thus friction welded together.

The rotor casing 4 'can be held stationary during friction welding using threaded fasteners passed through the protrusions 284 in the rotor casing 4' and into the cylindrical mounting block 516 (see Fig. 40).

After the upper bearing assembly 50 ′ is attached to the rotor housing 4 ′, the friction welding fixture 500 can be removed from the rotor housing 4 ′. The upper bearing assembly 50 ′ thus remains correctly positioned and attached to the rotor housing 4 ′, as shown in FIG. 41 of the accompanying drawings. It should be understood that the upper bearing assembly 50 'is placed in a position that is central to the lower circular shoulder 148' of the rotor housing 4 '. Accordingly, while the internal components of the cage 2 'are placed inside the casing 4', the abutment of the carrier plate 70 'to the specified shoulder 148' ensures that the lower bearing assembly 90 'is also centered with the specified shoulder 148'. The upper and lower bearing assemblies 50 ', 90' are thus axially aligned despite any previous deformation of the rotor casing 4 'that has occurred after injection molding.

The versatility of the improved separator is improved compared to the existing separator 2 due to some of its modules or components, interchangeable in various separator systems (see Fig. 36). The ability of the rotor casing 4 '(i.e., one particular type of module) to receive different valve assemblies 14' (i.e., different versions of another type of module) has already been discussed above. This model approach is achieved with different versions of this type of module or component (for example, valve assembly 14 ') having identical features for connecting or interfacing with other modules or components. For example, the separator system may potentially use one of several different versions of the valve assembly, as these various versions are provided with common features that can be mated to the rotor housing 4 'even though the valve assemblies may vary in many other respects. The table presented in FIG. 36 shows how the various components or modules of the separator system can be further provided with a component or module or replaced with a different version of the component or module.

The present invention is not limited to the specific embodiments described above. Alternative arrangements and suitable materials should be apparent to those skilled in the art.

Claims (10)

1. A gas cleaning separator (2 ') for separating a fluid mixture of substances of different densities, such as gas and liquid, containing:
a casing (4 ') forming the inner space,
a rotor assembly (78 ', 84', 86 ') for imparting a rotational motion to said mixture of substances, the rotor assembly comprising a plurality of separator disks (82') placed by a stack (84 ') rotating about one axis (64'), the rotor the assembly comprises an inlet (600) for receiving said mixture of substances, an outlet (604) from which these substances are discharged from the rotor assembly during use, and a path (602) for flow between adjacent separator disks to provide fluid communication between the inlet (600 ) and exit (604), and exit (604) is located more radially outwardly from said axis (64 ') than the inlet (600);
an opening for passing a fluid flow along a flow path between the outer part of said casing (4 ') and said inner space, and
a protrusion (6 ') protruding upward from the casing (4') and surrounding the specified hole;
characterized in that the protrusion (6 ') comprises a curved surface (221) extending inwardly into the hole, wherein
said separator (2 ') comprises a nozzle (22') that can be connected to said protrusion (6 ') so that the inner surface of the nozzle (22') is combined with the curved surface of the protrusion (6 ') to obtain a curved surface for said path for flow. 2. The separator (2 ') according to claim 1, in which the specified curved surface (221) forms a closed loop around the hole and goes inside the hole so as to reduce the area of the hole when moving through the specified hole from the outside of the specified casing (4') in the direction of the indicated interior space. 3. The separator (2 ') according to claim 2, in which the specified curved surface (221) describes a partially circular line when viewed in a transverse section made in a plane coinciding with the longitudinal axis (64') through the specified hole. 4. The separator (2 ') according to any one of claims 1 to 3, in which the protrusion (6') contains a generally cylindrical shape (217), the free end of which is provided with a circular protrusion (219) forming a curved surface (221). 5. The separator (2 ') according to any one of claims 1 to 3, which also contains a pipe (22'), which can be connected to the protrusion (6 ') so that the inner surface (216) of the pipe (22') is combined with a curved protrusion surface (6 ') to obtain a curved surface in transit. 6. The separator (2 ^' ) according to claim 5, in which the inner surface of the nozzle (216) meets the curved surface (221) on the edge (229) of the protrusion (6') and at this meeting point is oriented tangentially to the curved surface (221) ) 7. The separator (2 ') according to claim 5, in which the pipe (22') further comprises a curved wall (235) configured to fit the protrusion (6 ') to the curved surface (221). 8. The separator (2 ') according to any one of claims 6 or 7, in which the pipe (22') can be connected to the protrusion (6 ') for any orientation of rotation. 9. The separator (2 ') according to claim 8, in which the pipe (22') can be connected to the protrusion (6 ') by friction welding. 10. A method of assembling a gas treatment separator, wherein the separator (2 ') is a separator (2') according to any one of claims 5 to 9, this method comprising the step of connecting the nozzle (22 ') to the protrusion (6') by friction welding.

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