JP5992460B2 - Gas purifier separator - Google Patents

Description

  The present invention relates to a separator, and more particularly, but not exclusively, to a centrifuge for the cleaning of gaseous fluids.

  It is well known that fluid mixtures having different densities can be separated from each other through the use of a centrifuge. One special use of such a separator is in the separation of oil from gas discharged from the crankcase of an internal combustion engine.

  With this particular use of the separator, it is well understood that the high pressure gas found in the combustion chamber of an internal combustion engine tends to leak through the corresponding piston ring and into the engine crankcase. This continuous leakage of gas into the crankcase can lead to an undesirable increase in pressure within the case and, as a result, the need to exhaust gas from the case. In many commercial vehicles, the exhaust gas is generally reintroduced into the intake manifold of the engine. However, the gas discharged from the crankcase typically retains a large amount of engine oil (such as small droplets or fine mist) that has been withdrawn from a sump of oil retained in the crankcase. More specifically, the gas flowing between the engine cylinder and the corresponding piston tends to lift the lubricating oil located on the cylinder wall. Also, the condensation of oil vapor by the engine's cylinder block cooling system creates oil mist in the crankcase.

  To allow the introduction of the exhausted gas into the inlet system without the introduction of undesirable oils (especially into the turbocharger system, where the presence of caulking oil can favor the efficiency of the compressor) This requires cleaning the gas that was discharged before the gas was introduced into the inlet system (ie, removing the oil retained by the gas). This cleaning step may be performed by a centrifuge provided on or adjacent to the crank housing and directing the cleaned gas to the introduction system and returning the separated oil to the crankcase. I can do it.

  A centrifuge that has achieved the above-mentioned work with great commercial success is the applicant's ALFDEX® separator. This conventional separator will be described in detail below with reference to the accompanying drawings in order to clearly illustrate the improvements of the invention described subsequently.

  There are a number of problems associated with conventional ALFDEX® separators. These problems can be considered in three broad categories.

  First, the fluid path through the separator causes a pressure loss that adversely affects the flow rate of the separator and, as a result, adversely affects the dimensions of the engine that can be used with the separator. The first section of the problem associated with the conventional ALFDEX® separator is therefore related to the pressure loss in the fluid flow passage.

  Second, the structure of conventional separators can, under certain circumstances, cause the cleaned gas to become contaminated before leaving the separator. Thus, the second section of the problem associated with conventional separators relates to undesirable oil contamination of the cleaned gas.

  Third, certain manufacturing techniques and structural features associated with conventional separators can lead to assembly difficulties and / or reliability problems. Thus, the third category of problems associated with conventional separators relates to the manufacture and reliability of the separator.

  Each of these categories is discussed in more detail below.

The first concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ') defining an interior space; and disposed about said interior space and rotatable about a center line (64') to impart movement on the mixture of substances to be separated At least one vane element (116 ') which is
With
The leading edge (310) portion of the wing element (116 ') is, in use, such that the mixture of substances flowing toward the leading edge (310) portion is guided linearly with the wing element (116'). It is characterized by having a guide surface.

  Further features of the invention are provided in the separator as quoted below.

  As far as the first concept of the invention is concerned, the separator (2 ') as described above comprises a plurality of blade elements (116') spaced equally around the center line (64 ').

  As far as the first concept of the invention is concerned, the separator (2 ′) as described above comprises twelve blade elements (116 ′) located around the center line (64 ′).

  As far as the first concept of the present invention is concerned, the separator (2 ′) as described above comprises a portion where the guide surface is curved.

  As far as the first concept of the invention is concerned, the separator (2 ′) as described above is provided with a guide vane (314) whose guide surface extends from the front edge (310) portion.

  As far as the first concept of the present invention is concerned, the separator (2 ') as described above is such that the guide vanes (314) of the vane elements (116') have the vane elements (116 ') around the center line (64'). ) For a given rotational speed and for a given flow speed of the mixture, with respect to the vane element (116 ') so that the guide vanes (314) are substantially linear with the flow of the mixture. Arranged at an angle (322).

  As far as the first concept of the invention is concerned, the separator (2 ') as described above is rotatable about the center line (64') and receives the material from the vane element (116 '). It further comprises at least one separation disk (82 ') arranged in the space.

  As far as the first concept of the invention is concerned, the separators (2 ′) as described above are arranged in a stack (84 ′), can be rotated about the same center line (64 ′), and the vane elements (116). A plurality of separating disks (82 ') arranged in the space to receive the substance from').

  As far as the first concept of the present invention is concerned, the separator (2 ') as described above is such that the center line (64') of the separating disk (82 ') is the center line (64') of the blade element (116 '). Is consistent with.

The second concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities, such as gas and liquid, where the separator (2') is:
A housing (4 ') defining an internal space;
An inlet disposed in the interior space for imparting rotational movement onto the mixture of substances and rotatable about a center line (64 ') relative to a housing (4') for receiving the mixture of substances (600) comprising an outlet (604) through which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604). A rotating assembly (78 ', 84', 86 '), wherein the outlet (604) is located more radially outward from the centerline (64') than the inlet (600); An area (606) is defined for receiving the fluid discharged from the solid (78 ', 84', 86 ') and directing the fluid to the first outlet hole (10') of the housing (4 ', 70'). A housing member (72 ');
With
The inlet (610) to the region (606) comprises at least one longitudinal portion (612) of greater depth (613) than the other longitudinal portions of the inlet (610); It is characterized by.

  Further features of the present invention are provided in separators as cited below.

  As far as the second concept of the present invention is concerned, in the separator (2 ') as described above, the housing member (72') is adjacent to the end member (86 ') of the rotating assembly (78', 84 ', 86'). The region (606) is defined between the end member (86 ') and the housing member (72').

  As far as the second concept of the present invention is concerned, the separator (2 ′) as described above is such that the inlet (610) to the region (606) is the peripheral edge (274) of the end member (86 ′) and the housing member (72 ′). ).

  As far as the second concept of the present invention is concerned, the separator (2 ') as described above has a circular periphery at the periphery (274), and a longitudinal portion of the region inlet (610) extends along the edge (274). Extend in the direction.

  As far as the second concept of the invention is concerned, the separator (2 ') as described above has a longitudinal portion (612) of greater depth (613) along the edge (274) and the other longitudinal portion. In the periphery (274), providing a distance between the edge (274) and the end portion (86 ') along the longitudinal portion (612) that is larger than between the end portion (86') Is provided by a recess.

  As far as the second concept of the present invention is concerned, in the separator (2 ′) as described above, the circular peripheral edge (274) of the housing member (72 ′) is concentric with the center line (64 ′).

  As far as the second concept of the invention is concerned, the separator (2 ′) as described above has a longitudinal part (612) of greater depth (613) between 45 ° and 110 °, preferably 80 °, And has a partial circular shape extending through the arc (280).

  As far as the second concept of the present invention is concerned, the separator (2 ') as described above is such that the other longitudinal part is 1/10 and 1/2 the depth of the at least one longitudinal part (612). Having a depth between, and preferably having a depth of 1/3 of the depth of the at least one longitudinal portion (612).

  As far as the second concept of the invention is concerned, the separator (2 ') as described above is such that the at least one longitudinal portion (612) is the first outlet hole (10') of the housing (4 ', 70'). To the opposite side of the housing member (72 ').

  As far as the second concept of the invention is concerned, the separator (2 ') as described above is such that the at least one longitudinal portion (612) is the first outlet hole (10') of the housing (4 ', 70'). An opening is made in the path (272) defined by the housing member (72 ') for directing fluid to the outside.

  As far as the second concept of the invention is concerned, the separator (2 ′) as described above is such that the at least one longitudinal portion (612) is an inlet (282) to the path (272), the path (272) being The passage inlet (282) includes an element (276, 278) that, in use, is linear with the direction of fluid flowing into the passage inlet (282).

  As far as the second concept of the invention is concerned, the separator (2 ') as described above has the elements (276, 278) curved at the passage inlet (282) and the housing (4', 70 '). It is gradually straightened in the downstream direction toward the first outlet hole (10 ').

  As far as the second concept of the invention is concerned, the separator (2 ') as described above comprises the opposite side wall in which the elements (276, 278) define the path (272).

  As far as the second concept of the present invention is concerned, the separator (2 ') as described above has the housing member (72') adjacent to the end member (86 ') of the rotating assembly (78', 84 ', 86'). The region (606) and the path (272) are defined between the end member (86 ') and the housing member (72').

  As far as the second concept of the present invention is concerned, the separator (2 ') as described above is formed by the housing member (72') and the end member (86 ') of the rotating assembly (78', 84 ', 86'). The distance between is greater in one part of the region (606) than in the other part, so that the one part defines the path (272) in the housing member (72 ').

  As far as the second concept of the present invention is concerned, in the separator (2 ′) as described above, the path (272) is provided with a tubular portion (270).

The third concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ') defining an internal space;
An inlet disposed in the interior space for imparting rotational movement onto the mixture of substances and rotatable about a center line (64 ') relative to a housing (4') for receiving the mixture of substances (600) comprising an outlet (604) through which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604). A rotating assembly (78 ', 84'), wherein the outlet (604) is located more radially outward from the centerline (64 ') than the inlet (600); and the rotating assembly (78 ′, 84 ′) housing member (72) defining a region (606) for receiving the fluid discharged from the housing and directing the fluid toward the first outlet hole (10 ′) of the housing (4 ′, 70 ′). When;
With
The region (606) includes a path (272) extending from a portion of the periphery (274) of the housing member (72 '), the portion defining an inlet (282) to the path (272). It is characterized by that.

  Further features of the present invention are provided in the separator as quoted below.

  As far as the third concept of the present invention is concerned, the separator (2 ′) as described above is such that the path (272) flows into the path inlet (282) and into the path inlet (282) in use. With elements (276, 278) that are linear with the direction of the fluid that is present.

  As far as the third concept of the invention is concerned, the separator (2 ') as described above has the elements (276, 278) curved at the passage inlet (282) and the housing (4', 70 '). It is gradually straightened in the downstream direction toward the first outlet hole (10 ').

  As far as the third concept of the invention is concerned, the separator (2 ') as described above comprises the opposite wall where the elements (276, 278) define the path (272).

  As far as the third concept of the present invention is concerned, the separator (2 ′) as described above is such that the passage inlet (282) has a housing member (72) with respect to the first outlet hole (10 ′) of the housing (4 ′, 70 ′). It is arrange | positioned on the opposite side of ').

  As far as the third concept of the invention is concerned, the separator (2 ') as described above has an arc whose peripheral part defining the path inlet (282) is between 45 ° and 110 °, preferably 80 °. It has a partial circular shape extending through (280).

  As far as the third concept of the present invention is concerned, the separator (2 ') as described above has the housing member (72') adjacent to the end member (86 ') of the rotating assembly (78', 84 ', 86'). The region (606) and the path (272) are defined between the end member (86 ') and the housing member (72').

  As far as the third concept of the present invention is concerned, the separator (2 ') as described above is formed by the housing member (72') and the end member (86 ') of the rotating assembly (78', 84 ', 86'). The distance between is greater in one part of the region (606) than in the other part, so that the one part defines the path (272) in the housing member (72 ').

  As far as the third concept of the present invention is concerned, in the separator (2 ′) as described above, the path (272) is provided with a tubular portion (270).

The fourth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ') defining an internal space;
An inlet disposed in the interior space for imparting rotational movement onto the mixture of substances and rotatable about a center line (64 ') relative to a housing (4') for receiving the mixture of substances (600) comprising an outlet (604) through which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604). A rotating assembly (78 ', 84'), wherein the outlet (604) is located more radially outward from the centerline (64 ') than the inlet (600); and the rotating assembly (78 ′, 84 ′) housing member (72) defining a region (606) for receiving the fluid discharged from the housing and directing the fluid toward the first outlet hole (10 ′) of the housing (4 ′, 70 ′). When;
With
The region (606) comprises a path (272), the path (272) flowing into the inlet (282) to the path (272) and in use into the path inlet (282) It is characterized by having elements (276, 278) that are linear with the direction of.

  Further features of the present invention are provided in the separator as quoted below.

  As far as the fourth concept of the present invention is concerned, in the separator (2 ′) as described above, the path (272) extends from a part of the peripheral edge (274) of the housing member (72 ′), and the part is the path. An entrance (282) for (272) is defined.

  As far as the fourth concept of the invention is concerned, the separator (2 ′) as described above has the elements (276, 278) curved at the passage inlet (282) and the housing (4 ′, 70 ′). It is gradually straightened in the downstream direction toward the first outlet hole (10 ').

  As far as the fourth concept of the present invention is concerned, the separator (2 ') as described above comprises the opposite wall on which the elements (276, 278) define the path (272).

  As far as the fourth concept of the present invention is concerned, the separator (2 ′) as described above is such that the passage inlet (282) has a housing member (72) with respect to the first outlet hole (10 ′) of the housing (4 ′, 70 ′). It is arrange | positioned on the opposite side of ').

  As far as the fourth concept of the present invention is concerned, the separator (2 ') as described above has an arc whose peripheral part defining the path inlet (282) is between 45 ° and 110 °, preferably 80 °. It has a partial circular shape extending through (280).

  As far as the fourth concept of the present invention is concerned, the separator (2 ') as described above has the housing member (72') adjacent to the end member (86 ') of the rotating assembly (78', 84 ', 86'). The region (606) and the path (272) are defined between the end member (86 ') and the housing member (72').

  As far as the fourth concept of the present invention is concerned, the separator (2 ') as described above is formed by the housing member (72') and the end member (86 ') of the rotating assembly (78', 84 ', 86'). The distance between is greater in one part of the region (606) than in the other part, so that the one part defines the path (272) in the housing member (72 ').

  As far as the fourth concept of the present invention is concerned, in the separator (2 ′) as described above, the path (272) is provided with a tubular portion (270).

The fifth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ′, 70 ′) defining an internal space;
Arranged in the interior space for imparting rotational movement on the mixture of substances, rotatable about a center line (64 ') with respect to the housing (4', 70 ') and receiving the mixture of substances An inlet (600) for outlet, an outlet (604) from which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604) A rotating assembly (78 ', 84'), wherein the outlet (604) is located more radially outward from the centerline (64 ') than the inlet (600); A housing defining a region (606) for receiving fluid discharged from the solid (78 ', 84') and directing the fluid to the first outlet hole (10 ') of the housing (4', 70 ') A member (72 ');
With
The housing member (72 '), in use, is for isolating the inlet to the region (606) from fluid that flows past the inlet to the region (606) and then recirculates toward the inlet. Means (264) are provided.

  Further features of the present invention are provided in separators as cited below.

  As far as the fifth concept of the present invention is concerned, in the separator (2 ′) as described above, the separating means (264) is provided with a wall.

  As far as the fifth concept of the present invention is concerned, the separator (2 ′) as described above has the region (606) in the downstream direction with respect to the flow of the fluid that has passed through the inlet of the region (606) in use. ) It extends from the downstream side of the entrance.

  As far as the fifth concept of the present invention is concerned, the separator (2 ') as described above has the wall separated from the housing (4').

  As far as the fifth concept of the present invention is concerned, in the separator (2 ') as described above, the wall is provided with a free end (608).

  As far as the fifth concept of the present invention is concerned, the separator (2 ') as described above is such that the free end (608) has a centerline distance of between 2 mm and 200 mm in the centerline direction, and preferably a distance of 14 mm. Only away from the housing (4 ', 70') (456).

  As far as the fifth concept of the present invention is concerned, the separator (2 ′) as described above is such that the free end (608) is less than the center line distance in the direction perpendicular to the center line direction by the housing ( 4 ', 70').

  As far as the fifth concept of the invention is concerned, the separator (2 ') as described above defines a ring in which the wall is closed.

  As far as the fifth concept of the present invention is concerned, in the separator (2 ') as described above, the wall defines a truncated truncated cone shape.

  As far as the fifth concept of the invention is concerned, the separator (2 ') as described above has a longitudinal centerline where the truncated frustoconical shape coincides with the centerline (64') of rotation. .

  As far as the fifth concept of the present invention is concerned, the separator (2 ′) as described above has the truncated truncated cone shape in the downstream direction related to the flow of the fluid that has passed through the inlet of the region (606) in use. Is diverging.

  As far as the fifth concept of the present invention is concerned, the separator (2 ') as described above is a means for the housing member (72') to support the housing member (72 ') relative to the housing (4', 70 '). (266), and the support means (266) is arranged downstream of the isolating means (264) for the flow of fluid that has passed through the region (606) inlet in use.

  As far as the fifth concept of the invention is concerned, the separator (2 ') as described above is a wall defining a ring with the support means (266) closed.

  As far as the fifth concept of the present invention is concerned, in the separator (2 ′) as described above, the wall has a cylindrical shape.

  As far as the fifth concept of the invention is concerned, the separator (2 ') as described above has a longitudinal centerline in which the wall coincides with the centerline (64') of rotation.

  As far as the fifth concept of the invention is concerned, the separator (2 ′) as described above has at least one hole (454) in the wall at the intersection between the wall and the housing (4 ′, 70 ′). Is provided.

  As far as the fifth concept of the present invention is concerned, the separator (2 ′) as described above further comprises a second outlet hole of the housing (4 ′, 70 ′), in which the support means (266) is the second outlet hole. 2 is disposed in the fluid flow path between the outlet hole and the isolation means (264).

  As far as the fifth concept of the present invention is concerned, in the separator (2 ') as described above, the second outlet hole is arranged concentrically with the center line (64') of rotation.

  As far as the fifth concept of the present invention is concerned, in the separator (2 ′) as described above, when the isolating means (264) is in use, the fluid flowing through the inlet of the area (606) is the isolating means. It is arranged in the housing (4 ′, 70 ′) so that the fluid flowing on one side of (264) and recirculating flows on the other side of the isolating means (264).

  As far as the fifth concept of the present invention is concerned, the separator (2 ′) as described above carries the fluid from the region (606) to the outside of the housing (4 ′, 70 ′) through the outlet hole (10 ′). For this purpose, an outlet conduit (211) extends between the housing member (72 ') and the housing (4', 70 ') so that fluid can flow freely over the entire outer circumference of the outlet conduit (211). As such, the exterior of the outlet conduit (211) is remote from the housing (4 ', 70').

  As far as the fifth concept of the present invention is concerned, in the separator (2 ′) as described above, the outlet conduit (211) is different from the housing member (72 ′) and the housing (4 ′, 70 ′).

The sixth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different density such as gas and liquid, the separator (2') being:
A housing (4 ') defining an internal space;
A hole for allowing fluid flow along the flow path between the exterior of the housing (4 ') and the interior space; and a shoulder (6) rising from the housing (4') and surrounding the hole When;
With
The shoulder (6 ') is characterized by a curved surface (221) extending inwardly into the hole.

  Further features of the present invention are provided in separators as cited below.

  As far as the sixth concept of the invention is concerned, the separator (2 ') as described above forms a ring in which the curved surface (221) is closed around a hole and the housing (4') Extending inwardly into the hole so that the area of the hole decreases when moved from the outside to the internal space through the hole.

  As far as the sixth concept of the invention is concerned, the separator (2 ′) as described above is obtained through a plane in which the curved surface (221) coincides with the longitudinal center line (64 ′) through the hole. Draw a partial circular line when viewed in a cross section.

  As far as the sixth concept of the invention is concerned, the separator (2 ′) as described above has a shoulder (6 ′) with a generally cylindrical wall (217), with a curved surface (221) at its free end. A circumferential lip (219) is provided.

  As far as the sixth concept of the present invention is concerned, the separator (2 ′) as described above further comprises a nipple (22 ′) connectable to the shoulder (6 ′), and the inner surface (216) of the nipple (22 ′). ) In combination with the curved surface (221) of the shoulder (6 ') provides a curved surface for the flow path.

  As far as the sixth concept of the invention is concerned, the separator (2 ′) as described above encounters a surface (221) whose inner nipple surface (216) is curved at the edge (229) of the shoulder (6 ′), and this At the point of encounter, it is directed as a tangent to the curved surface (221).

  As far as the sixth concept of the present invention is concerned, the separator (2 ') as described above has a curved wall configured so that the nipple (22') abuts the curved surface (221) of the shoulder (6 '). (235) is further provided.

  As far as the sixth concept of the present invention is concerned, the separator (2 ') as described above can be connected to the shoulder (6') in any rotation direction of the nipple (22 ').

  As far as the sixth concept of the present invention is concerned, in the separator (2 ′) as described above, the nipple (22 ′) can be connected to the shoulder (6 ′) by rotary welding.

  The seventh concept of the present invention provides a method of assembling a gas cleaning separator (2 '), which comprises the step of connecting the nipple (22') to the shoulder (6 ') by rotary welding, and separating the separation. The machine is as described above as far as the sixth concept of the invention is concerned.

The eighth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of different density substances such as gases and liquids, the separator (2') being:
A housing (4 ') defining an internal space;
An inlet disposed in the interior space for imparting rotational movement onto the mixture of substances and rotatable about a center line (64 ') relative to a housing (4') for receiving the mixture of substances (600) comprising an outlet (604) through which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604). A rotating assembly (78 ', 84'), wherein the outlet (604) is located more radially outward from the centerline (64 ') than the inlet (600);
Defining a region (606) for receiving fluid discharged from the rotating assembly (78 ', 84') and directing the fluid to the first outlet hole (10 ') of the housing (4', 70 '); A housing member (72 ');
With
Between the housing member (72 ') and the housing (4', 70 ') for transporting fluid from the region (606) to the outside of the housing (4', 70 ') through the outlet hole (10') The outlet conduit (211) extends outside the outlet conduit (211) so that fluid can flow freely around the entire circumference of the outlet conduit (211). It is characterized by being away from ′).

  Further features of the present invention are provided in separators as cited below.

  As far as the eighth concept of the present invention is concerned, the separator (2 ′) as described above is directed to the housing member (72 ′) after flowing through the inlet to the region (606) in use. Means (264) are provided for isolating the inlet to the region (606) from recirculating fluid and the outlet conduit (211) extends from the isolating means (264).

  As far as the eighth concept of the invention is concerned, in the separator (2 ') as described above, the separating means (264) comprises a wall, which preferably comprises a free end (608) and the housing. (4 ', 70').

  As far as the eighth concept of the present invention is concerned, in the separator (2 ′) as described above, the outlet conduit (211) is different from the housing member (72 ′) and the housing (4 ′, 70 ′).

The ninth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ') defining an internal space;
Positioned in the interior space for imparting rotational movement onto the mixture of substances, rotatable about a center line (64 ') relative to a housing (4') and adapted to receive the mixture of substances A first inlet (600), a first outlet (604) from which the substance is discharged during use, and a first fluid communication for providing fluid communication between the first inlet (600) and the first outlet (604). A rotating assembly (1) comprising a flow path (602), wherein the first outlet (604) is located more radially outward from the center line (64 ') than the first inlet (600); 78 ', 84'); and a housing member (72 ') disposed adjacent to the rotating assembly (78', 84 ');
With
The housing member and rotating assembly define a first fluid flow route for fluid discharged from the rotating assembly (78 ', 84') on the first side of the housing member (72 ') therebetween. The housing member (72 ') is also spaced apart from the housing (4') on the second side of the housing member (72 ') and between them the rotating assembly (606). 78 ′, 84 ′) providing a second region (614) defining a second fluid flow route for the fluid discharged from
The rotating assembly (78 ′, 84 ′) is provided through a second inlet (618) and a second inlet (618) that are opened into the second region (614) on the second side of the housing member (72 ′). Also provides a second outlet (620) located more radially outward from the centerline (64 ') and fluid communication between the second inlet (618) and the second outlet (620). The second flow path (616) is provided.

  Further features of the present invention are provided in separators as cited below.

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above has the second outlet (620), the first outlet (604), the first and second regions (606, 614), Open into a fluid conduit providing fluid communication between the two.

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above relates to the flow of the substance that the second outlet (620) is discharged from the first outlet (604) during use. It is open at a position downstream of the first outlet (604) and upstream of the first and second regions (606, 614).

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, each of the second flow paths (616) has a disk-shaped portion and is centered on the center line (64 ′). A space is provided between the first and second members (86 ', 240) of the rotating assembly being placed.

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above has a disk-shaped portion of the member (86 ′, 240) having a substantially circular radially outer edge. The two members (86 ', 240) are positioned concentrically with each other.

  As far as the ninth concept of the present invention is concerned, the separator (2 ') as described above is located in the space when the rotating assembly is rotated around the center line (64') in use. At least one elongate element (298) is disposed in the space between the first and second members (86 ', 240) so as to move the fluid present outward relative to the centerline (64') .

  As far as the ninth concept of the invention is concerned, the separator (2 ') as described above has an elongated element (298) extending radially along the second flow path (616).

  As far as the ninth concept of the invention is concerned, the separator (2 ') as described above has an elongated element (298) provided on one of the first and second members (86', 240), and the first and second It is in contact with the other of the second members (86 ', 240).

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, the disk-shaped portions of the individual members (86 ′, 240) have a truncated truncated cone shape.

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, the second flow path (616) has a truncated truncated cone shape.

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, the first flow path (602) has a truncated truncated cone shape.

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above has the second inlet (618) of the second flow path (616) centered on the center line (64 ′). It has a ring shape.

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above has the second flow path (616) between the first and second sides of the housing member (72 ′). ) It extends through the hole inside.

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, the second inlet (618) of the second flow path (616) is defined by a substantially cylindrical wall (300).

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above has at least one of the part of the housing member (72 ′) defining the hole therein and the second flow path (616). A space is provided between the first part (300) of the rotating assembly defining the site, and a further part (304) of the rotating assembly covers the first part (300) so as to cover the space. ).

  As far as the ninth concept of the invention is concerned, in the separator (2 ′) as described above, the further part (304) is arranged on the second side of the housing member (72 ′).

  As far as the ninth concept of the invention is concerned, the separator (2 ') as described above has the further part (304) extending from the second inlet (618).

  As far as the ninth concept of the invention is concerned, in the separator (2 ′) as described above, the further part (304) has an annular shape.

  As far as the ninth concept of the present invention is concerned, the separator (2 ') as described above is such that the further part (304) has an outer circular periphery with a diameter larger than the diameter of the hole in the housing member (72'). have.

  As far as the ninth concept of the present invention is concerned, the separator (2 ') as described above is oriented in a plane in which the further part (304) is flat and the center line (74') is orthogonal thereto. It has been.

  As far as the ninth concept of the present invention is concerned, the separator (2 ′) as described above defines the second flow path (616), and the surface extending from the second inlet (618) has the two flow paths. Concentrate on the center line (64 ') when moving from the second inlet (618) to the second outlet (620) along a path (616) in a radial direction relative to the center line (64') It has the outermost part (302).

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, the radially outermost portion (302) of the surface of the second flow path has a truncated truncated cone shape.

  As far as the ninth concept of the present invention is concerned, in the separator (2 ′) as described above, the truncated frustoconical shape of the outermost part (302) in the radial direction is the center line (64 ′) of rotation. It has a matching central longitudinal centerline.

The tenth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities, such as gas and liquid, where the separator (2') is:
A housing (4 ′, 70 ′) defining an internal space;
Arranged in the interior space for imparting rotational movement on the mixture of substances, rotatable about a center line (64 ') with respect to the housing (4', 70 ') and receiving the mixture of substances An inlet (600) for outlet, an outlet (604) from which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604) A rotating assembly (78 ', 84'), wherein the outlet (604) is located more radially outward from the centerline (64 ') than the inlet (600);
With
The rotating assembly (78 ′, 84 ′) further includes a rotating shaft (78 ′) that is aligned with the center line (64 ′) and provided on the housing (4 ′, 70 ′), Here, the first end portion of the rotating shaft (78 ′) passes through the housing (4 ′, 70 ′) and extends to a position outside the housing (4 ′, 70 ′), and A fluid passage (92 ') extends axially through the rotating shaft (78') and has an opening located outside the housing (4 ', 70');
Flow control means (364, 366) for controlling the fluid that the rotating assembly (78 ', 84') enters the axial fluid passage (92 ') from the outside of the housing (4', 70 ') is further provided. Wherein flow control means (364, 366) provide rotational movement along the passage radially outward from the axial fluid passage (92 ') onto the fluid entering the passage (92'). It is characterized by having means for granting.

  Further features of the present invention are provided in separators as cited below.

  As far as the tenth concept of the invention is concerned, the separator (2 ') as described above is centered on the centerline (64') of the rotational movement of the rotary assembly (78 ', 84'). ing.

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above has the passage (92') coincident with the center line (64 ') of the rotation of the rotating assembly (78', 84 '). ing.

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above is such that the means for imparting rotational motion on the fluid is the centerline of rotation of the rotating assembly (78', 84 '). At least one fluid passage (366) located radially outward from (64 ').

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above is a member (364) in which the means for imparting rotational motion on the fluid is separated from the opening of the axial fluid passage (92'). Wherein at least one fluid passage (366) is a hole extending through said member (364).

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above has four fluid passages (366) along the circumference of a circle centered on the center line (64'), etc. Located at intervals.

  As far as the tenth concept of the invention is concerned, the separator (2 ') as described above is oriented so that the member (364) is flat and the center line (64') is orthogonal thereto.

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above has the flow control means positioned more radially outward from the center line (64') than the fluid passage (366). And at least one discharge hole (368).

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above has a turbine (88') for driving the rotation of the flow control means (364, 366) and the rotating assemblies (78 ', 84'). ) Is a single component.

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above is provided with the second end portion of the rotating shaft (78') far from the first end portion with respect to the housing (4 ', 70'). It has been.

  As far as the tenth concept of the present invention is concerned, in the separator (2 ') as described above, the fluid passage (92') extends between the first and second ends of the rotating shaft (78 ') and the housing (4', 70 ') to provide fluid communication therethrough between the exterior and interior.

  As far as the tenth concept of the invention is concerned, the separator (2 ') as described above has a fluid passage (92') whereby the second end portion of the rotary shaft (78 ') is connected to the housing (4', 70 '). ) In fluid communication with a bearing (50 ') provided therewith.

  As far as the tenth concept of the present invention is concerned, the separator (2 ') as described above has a fluid passageway (92') in fluid communication with the inlet (600) of the rotating assembly.

The eleventh concept of the present invention provides a method of assembling a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') ,
A housing (4 ′, 12 ′) defining an internal space;
A hole (8 ') in the housing (4', 70 ') for providing fluid communication between the internal space and the exterior of the housing (4', 12 ');
A fluid flow conduit (22 ') sealed with respect to the hole (8');
With
A fluid flow conduit (22 ') is used to transport fluid between the interior space and the exterior of the housing (4', 12 ') via the conduit (22') and a hole (8 '). Fluid connection with hole (8 '),
A method of assembling the separator (2 ′)
The material of the housing (4 ', 12') and the fluid flow conduit (22 ') along the ring formed and closed by the intersection of the abutment surfaces of the housing (4', 12 ') and the fluid flow conduit (22') It has the process of joining together.

  Further features of this invention are provided in the methods as cited below.

  As far as the eleventh concept of the invention is concerned, in the method as described above, the closed ring is circular.

  As far as the eleventh concept of the present invention is concerned, the method as described above is such that the joining step causes the housing (4 ', 12') and the fluid flow conduit (22 ') to move relative to each other while their surfaces abut one another. It is equipped with rotating.

  As far as the eleventh concept of the invention is concerned, the method as described above is such that the relative rotation of the housing (4 ', 12') and the fluid flow conduit (22 ') is such that the housing (4', 12 ') and the flow conduit. (22 ') is stopped by being placed in a desired position relative to each other allowing the abutment surfaces to join together.

  As far as the eleventh concept of the invention is concerned, the method as described above comprises that the joining step rotationally welds the abutting surfaces together.

  As far as the eleventh concept of the invention is concerned, the method as described above comprises that the joining step applies an adhesive to at least one of the abutting surfaces.

  As far as the eleventh concept of the invention is concerned, the method as described above comprises that the joining step involves ultrasonic welding or vibration welding of the abutting surfaces to each other.

  As far as the eleventh concept of the invention is concerned, the method as described above is such that the fluid flow conduit (22 ') has an open end for further connection with a further fluid flow conduit, such as a hose, away from the abutment surface. It is a nipple provided.

The twelfth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ′, 12 ′) defining an internal space;
A hole (8 ') in the housing (4', 70 ') for providing fluid communication between the internal space and the exterior of the housing (4', 12 ');
A fluid flow conduit (22 ') sealed with respect to the hole (8');
With
A fluid flow conduit (22 ') is used to transport fluid between the interior space and the exterior of the housing (4', 12 ') via the conduit (22') and a hole (8 '). Fluid connection with hole (8 '),
A ring in which the material of the housing (4 ', 12') and the fluid flow conduit (22 ') is formed and closed by the intersection of the abutment surfaces of the housing (4', 12 ') and the fluid flow conduit (22') It is characterized by being joined together along the line.

  Further features of the present invention are provided in separators as cited below.

  As far as the twelfth concept of the present invention is concerned, in the separator as described above, the closed ring is circular.

  As far as the twelfth concept of the present invention is concerned, the separator as described above is such that the joints move the housing (4 ', 12') and the fluid flow conduit (22 ') relative to each other while their surfaces abut one another. It is done by rotating it automatically.

  As far as the twelfth concept of the present invention is concerned, the separator as described above is such that the relative rotation of the housing (4 ', 12') and the fluid flow conduit (22 ') is such that the housing (4', 12 ') and the flow. The conduit (22 ') is stopped by being placed in a desired position relative to each other allowing the abutment surfaces to join together.

  As far as the twelfth concept of the present invention is concerned, in the separator as described above, the joining is performed by rotationally welding the contact surfaces to each other.

  As far as the twelfth concept of the present invention is concerned, in the separator as described above, the joining is performed by applying an adhesive to at least one of the abutting surfaces.

  As far as the twelfth concept of the present invention is concerned, in the separator as described above, the joining is performed by ultrasonic welding or vibration welding of the contact surfaces to each other.

  As far as the twelfth concept of the present invention is concerned, the separator as described above is such that the fluid flow conduit (22 ') has an open end for further connection with a further fluid flow conduit, such as a hose, away from the abutment surface. It is a nipple provided for.

The thirteenth concept of the present invention provides a method of assembling a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') ,
A housing (4 ', 70') comprising first and second individual parts (4 ', 70');
An alignment surface (632) possessed by the first housing part (4 ');
A reference surface (630) that the second housing part (70 ') has and defines an internal space of the housing (4', 12 ') relative to the alignment surface (632);
A rotating assembly (78 ', 84) disposed in the internal space and rotatable about the center line (64') of the first housing part (4 ') relative to the housing (4', 70 '). When,
The rotating assembly (78 ', 84') is provided and is rotatably provided to the first housing part (4 ') by the bearing unit (50') and rotates with respect to the second housing part (70 '). A rotational axis (78 ′) provided in a possible manner;
With
A method of assembling the separator (2 ′)
The reference surface that coincides with the center line (64 ') when the reference surface (630) of the second housing part (70') is aligned with the alignment surface (632) of the first housing part (4 ') Providing a rotary shaft (78 ') rotatably with respect to the second housing part (70') at a predetermined position relative to (630);
A reference surface (634) for alignment with the alignment surface (632) of the first housing part (4 ') and for receiving the bearing unit (50') at a position relative to the reference surface (634) The bearing unit (50 ′) is disposed on a jig (500) including the means (512), and the reference surface (634) of the jig (500) is aligned with the first housing part (4 ′). The bearing unit (50 ′) is received by the jig (500) at a position relative to the reference surface (634) of the jig (500) that is aligned with the center line (64 ′) when aligned with the surface (632). The process of making it possible to
Positioning the reference surface (634) of the jig (500) to align with the alignment surface (632) of the first housing part (4 '); and
Fixing the bearing unit (50 ') to the first housing part (4');
It is characterized by having.

  Further features of this invention are provided in the methods as cited below.

  As far as the thirteenth concept of the present invention is concerned, in the method as described above, the step of fixing the bearing unit (50 ') is such that the reference surface (634) of the jig (500) is positioned in the first housing part (4'). While being aligned with the mating surface (632), the receiving means (512) of the jig (500) is moved in the direction of the center line along the center line (64 ') with respect to the first housing part (4'). Thus, the bearing unit (50 ′) comes into contact with the first housing part (4 ′).

  As far as the thirteenth concept of the present invention is concerned, in the method as described above, the receiving means (512) is moved in the direction of the center line with respect to the reference surface (634) of the jig (500) to move the bearing unit (50 ') to the first. Press against the housing part (4 ').

  As far as the thirteenth concept of the invention is concerned, the method as described above is such that the jig (500) is a receiving means in the central direction along the center line (64 ') with respect to the reference surface (634) of the jig (500). A means for allowing the movement of (512) is provided.

  As far as the thirteenth concept of the present invention is concerned, in the method as described above, the step of fixing the bearing unit (50 ') is such that the reference surface (634) of the jig (500) is positioned at the position of the first housing part (4'). Rotating the receiving means (512) of the jig (500) about the first housing part (4 ') about the center line (64') while being aligned with the mating surface (632). ing.

  As far as the thirteenth concept of the invention is concerned, the method as described above comprises the step of fixing the bearing unit (50 ') comprising rotationally welding the bearing unit (50') to the first housing part (4 '). ing.

  As far as the thirteenth concept of the invention is concerned, the method as described above comprises means for allowing the jig (500) to rotate the receiving means (512) relative to the reference surface (634) of the jig (500). Yes.

  The fourteenth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities, such as gas and liquid, where the separator (2') is As far as the thirteenth concept of the present invention is concerned, it is assembled as described above.

The fifteenth concept of the present invention provides a method of assembling a system comprising a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, wherein The method comprises the steps of selecting a particular type of first type component (4 ′) from a plurality of different types of first type component (4 ′) and said first type component (4 ′). ′) Connecting the specific mold with a second type of component (12 ′),
The plurality of different types of the first type of component (4 ') have common features (207, 211) for coupling with the second type of component (12'); It is characterized by.

  Further features of this invention are provided in the methods as cited below.

  As far as the fifteenth concept of the invention is concerned, the method as described above selects a specific type of the second type of component (12 ') from a plurality of different types of the second type of component (12'). The process of carrying out is further provided.

  As far as the fifteenth concept of the present invention is concerned, the method as described above further comprises the step of placing a third type of component between the first and second types of components (4 ′, 12 ′).

  As far as the fifteenth concept of the present invention is concerned, the method as described above further comprises the step of selecting the third type of component from a plurality of different types of the third type of component, wherein: The plurality of different types of the third type of components have a common feature for connecting with the first and second types of components (4 ', 12').

  As far as the fifteenth concept of the present invention is concerned, in the method as described above, the first type of component includes a rotating body housing (4 '), and the second type of component includes a valve unit housing (12'). And the third type of component comprises a heat shield.

  As far as the fifteenth concept of the invention is concerned, in the method as described above, the components are those of the separator (2 ′).

  As far as the fifteenth concept of the present invention is concerned, the method as described above is further adapted to connect the plurality of different types of the one type of component (4 ') with the fourth type of component (22'). It has a common feature (6 ').

  As far as the fifteenth concept of the invention is concerned, in the method as described above, the fourth type of component (22 ') is a nipple (22').

  The sixteenth concept of the present invention provides a kit of parts for assembling into a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gases and liquids, where The kit of parts includes a plurality of first-type components (4 ′) of the separator (2 ′) for connection with a second-type components (12 ′) of the separator (2 ′). A different type and at least one type of the second type of component (12 '), wherein the plurality of different types of the first type of component (4') are the second type. It is characterized by having common features (207, 211) for connecting with the type of component (12 '). Ideally, the different types of the first type of component (4 ') comprise a further common feature (6') for coupling with a third type of component (22 '). Yes.

The seventeenth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, where the separator (2') is:
A housing (4 ') defining an internal space;
A rotating assembly (78 ', 84') disposed in the interior space to impart rotational motion onto the mixture of materials and rotatable about a centerline (64 ') relative to a housing (4') And a valve structure disposed in the interior space defined by the valve unit housing (12 '), separated from the mixture of substances from the outlet (10') of the housing (4 ') A valve unit (14 ′) for controlling the flow of the material,
With
The valve unit housing (12 ′) is distinct from the rotating assembly housing (4 ′).

The eighteenth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ′, 70 ′) defining an internal space;
A rotating assembly disposed in the internal space and rotatable about a center line (64 ') with respect to the housing; and a housing member (72') provided in the housing (4 ', 70') ,
With
The housing member (72 ') allows fluid flow to either side of the housing member (72'), and fluid flowing on one side of the member (72 ') is allowed to flow into the housing (4' by the member). , 70 ′) through the first outlet hole (10 ′) and directed to the outside of the housing (4 ′, 70 ′),
The fluid is directed to the exterior of the housing via an outlet conduit (211) connected to the housing member (72 '), the outlet conduit (211) being connected to the housing member (72') and the housing (4 ', 70). It is characterized in that it is sealed by a sealing element provided for the outlet conduit (211) for at least one of ').

  Further features of the present invention are provided in separators as cited below.

  As far as the eighteenth concept of the present invention is concerned, in the separator (2 ') as described above, the outlet conduit (211) is separated from the housing (4', 70 ').

  As far as the eighteenth concept of the present invention is concerned, the separator (2 ') as described above has the outlet conduit (211) separate from the housing member (72') and sealed against it by a sealing element (215). ing.

  As far as the eighteenth concept of the present invention is concerned, the separator (2 ') as described above is different from the housing (4', 70 ') in that the outlet conduit (211), whereas it is separated by a sealing element (213). Sealed.

  As far as the eighteenth concept of the present invention is concerned, the separator (2 ') as described above is such that a sealing element for sealing the outlet conduit (211) is defined by the surface on the outer surface of the conduit. It is provided by contact.

  As far as the eighteenth concept of the present invention is concerned, the separator (2 ') as described above has a structure in which the outlet conduit (211) controls the flow of fluid from the housing (4', 70 '). , 70 ') and a valve unit (14') arranged outside.

  As far as the eighteenth concept of the present invention is concerned, in the separator (2 ') as described above, the sealing element is an O-ring sealing member.

  As far as the eighteenth concept of the present invention is concerned, the separator (2 ′) as described above has the outlet conduit (211) separated from the housing (4 ′, 70 ′), and the housing member (72 ′) and the above-mentioned The fluid located between the housings (4 ', 70') is allowed to flow around its entire circumference.

The nineteenth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities, such as gas and liquid, where the separator (2') is:
A housing (4 ') defining an internal space;
Positioned in the interior space for imparting rotational movement on the mixture of substances, rotatable about a center line (64 ') with respect to the housing (4'), the center line (64 ') of rotation A rotary disk (78 ') having a longitudinal center line coinciding with the hole (252) is provided, and the separator disk is provided on the rotary axis (78') by the hole (252) (82 '), an inlet (600) for receiving the mixture of substances, an outlet (604) from which the substance is discharged during use, and fluid communication between the inlet (600) and outlet (604) A rotating assembly () having a flow path (602) for providing the outlet, wherein the outlet (604) is located more radially outward from the center line (64 ′) than the inlet (600). 78 ′, 84 ′);
With
The rotating shaft (78 ') includes at least one spline (254), and a hole (252) in the separator disk (82') connects the rotating shaft (78 ') and at least one spline (254). It has a shape corresponding to a cross section taken through and perpendicular to the center line (64 ').

  Further features of the present invention are provided in separators as cited below.

  As far as the nineteenth concept of the present invention is concerned, the separator (2 ') as described above is provided on a central hub (114') having at least one spline (254) coupled to the rotating shaft (78 '). Yes.

  As far as the nineteenth concept of the present invention is concerned, the separator (2 ') as described above is provided with three splines (254).

  As far as the nineteenth concept of the invention is concerned, the separator (2 ') as described above comprises a tip portion (352) and a radial direction in which at least one spline (254) provides a free end to the spline (254). The tip portion (352) has an inner root portion (350), and the root portion (350) has a larger circumferential dimension than the tip portion (352).

  As far as the nineteenth concept of the present invention is concerned, the separator (2 ′) as described above has different circumferential dimensions of the root portion (350) and the tip portion (352), the root portion (350) and the tip portion (352). Steps (354) are provided on either side of the at least one spline (254) at the intersection between and.

  As far as the nineteenth concept of the present invention is concerned, in the separator (2 ') as described above, the circumferential dimension of the root portion (350) varies along the centerline length of at least one spline (254).

  As far as the nineteenth concept of the present invention is concerned, in the separator (2 ′) as described above, the separator disk (82 ′) has a truncated truncated cone shape.

  As far as the nineteenth concept of the present invention is concerned, in the separator (2 ') as described above, the spline extends in the center line direction along the length of the rotating shaft (78').

The twentieth concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ') defining an internal space;
An inlet disposed in the interior space for imparting rotational movement onto the mixture of substances and rotatable about a center line (64 ') relative to a housing (4') for receiving the mixture of substances (600) comprising an outlet (604) through which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604). A rotating assembly (78 ', 84'), further comprising a rotating shaft (78 ');
With
The rotating shaft (78 ') is provided with a coating of plastic material along the length of the rotating shaft (78') slidably receiving at least one component of the separator (2 '). It is characterized by that.

  As far as the twentieth concept of the present invention is concerned, in the separator (2 ') as described above, at least one of the components is made of a metal material.

  As far as the twentieth concept of the present invention is concerned, in the separator (2 ′) as described above, at least one of the components is a helical spring.

  As far as the twentieth concept of the present invention is concerned, in the separator (2 ′) as described above, at least one of the components is a bearing unit (50 ′).

  As far as the twentieth concept of the present invention is concerned, the separator (2 ') as described above receives two of the components on the opposite end portion of the rotating shaft (78'). Here, the individual components are helical springs (130 ', 96').

  As far as the twentieth concept of the present invention is concerned, the separator (2 ') as described above has an individual spiral spring (130', 96 '), a rotating assembly (78', 84 ') and a rotating shaft (78'). Is compressed between different ones of the two bearing units (50 ', 90') connecting the housing to the housing (4 ').

  As far as the twentieth concept of the present invention is concerned, in the separator (2 ′) as described above, the individual helical springs (130 ′, 96 ′) are made of a metal material.

  As far as the twentieth concept of the present invention is concerned, the separator (2 ') as described above is a material in which the rotating shaft (78') is not cured.

  As far as the twentieth concept of this invention is concerned, the separator (2 ') as described above is an unhardened metal, and preferably an unhardened steel.

  As far as the twentieth concept of the present invention is concerned, the separator (2 ′) as described above has at least one element (114 ′) in which the rotating assembly (78 ′, 84 ′) extends from the rotating shaft (78 ′). 116 ′, 254), wherein the elements (114 ′, 116 ′, 254) are of the same material as the coating and are formed integrally therewith.

  As far as the twentieth concept of the present invention is concerned, the separator (2 ′) as described above is such that the coating and the at least one element (114 ′, 116 ′, 254) are injection-molded on the rotating shaft (78 ′). And thereby formed simultaneously with each other.

The twenty-first concept of the present invention provides a gas clean separator (2 ') for separating flowable mixtures of substances of different densities such as gas and liquid, the separator (2') being:
A housing (4 ') defining an internal space;
An inlet disposed in the interior space for imparting rotational movement onto the mixture of substances and rotatable about a center line (64 ') relative to a housing (4') for receiving the mixture of substances (600), an outlet (604) through which the substance is discharged during use, and a flow path (602) for providing fluid communication between the inlet (600) and outlet (604). Rotating assemblies (78 ″, 84 ′);
With
A separator (2 ') receives an electric motor (380) for rotating the rotary assembly (78 ", 84') and, in use, material separated from the mixture of substances. It further includes a fluid passage that has passed through the electric motor (380).

  Further features of the present invention are provided in separators as cited below.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above is such that the fluid passage that has passed through the electric motor (380) is at least partially part of the rotor (382) of the electric motor (380) and It is defined by the stator (400).

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ′) as described above, the fluid passage has a space between the rotor (382) and the stator (400) of the electric motor (380). Yes.

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ′) as described above, the rotor (382) is connected to the rotating assembly (78 ″, 84 ′).

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ′) as described above, the electric wire arranged in the fluid passage is sealed with an insulating material.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ′) as described above is provided as a layer in which the insulating material covers the electric wires of the stator (400).

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ′) as described above, the insulating material comprises an epoxy lacquer.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above comprises one or more electronics arrangements in which an electric motor is sealed from the fluid passage through the electric motor (380). It has elements.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above comprises a housing (384) in which an electric motor (380) is arranged.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ′) as described above has the electric motor housing (384) in which the rotating assembly (78 ″, 84 ′) is disposed. 4 ′) and separable from the housing (4 ′).

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above has an electric motor housing (384) sealed from the fluid passage and an electronic component of the electric motor (380) therein. (408) is provided with a partitioned portion.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ′) as described above is the same as the rotary assembly (78 ″, 84 ′) in the separator (2 ′) in which the partitioned part is assembled. It has a substantially ring shape or a partial ring shape that is concentric with.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above is such that the partitioned part is separated from and sealed to the electric motor housing (384) and from the housing (384). It is surrounded by a member (394).

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ′) as described above, the member (394) has a substantially ring shape or a truncated truncated cone shape.

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ′) as described above, the member (394) is arranged concentrically with the rotary assembly (78 ″, 84 ′).

  As far as the twenty-first concept of the invention is concerned, the separator (2 ') as described above is sealed against the electric motor housing (384) along a ring in which the radially inner part of the member (394) is closed. And the radially outer portion of the member (394) is sealed to the electric motor housing (384) along a further closed ring.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above is such that the radially inner portion of the member (394) is in comparison with the substantially cylindrical portion (392) of the electric motor housing (384). The rotary assembly (78 ″, 84 ′) extends in the substantially cylindrical portion (392), which is sealed, in the assembled separator.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ′) as described above is such that the radially inner part of the member (394) is the innermost part of the stator (400) of the electric motor (380). A hole having a diameter smaller than or substantially equal to the diameter is defined.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ′) as described above has an electric wire extending through the member (394), and the electric wire is sealed against it, at least. One hole is provided.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above has one or more components for controlling the operation of the electric motor (380) by the one or more electronic components. It has the following components.

  As far as the twenty-first concept of the present invention is concerned, in the separator (2 ') as described above, the fluid passage is in fluid communication with the outlet hole (402) in the electric motor housing (384).

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above further comprises an electrical connector (412) for receiving electrical wires that provide power and / or control signals to the electric motor (380). Yes.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above has an electrical connector (412) electrically connected to an electric motor (380) by one or more electrical components (408). ing.

  As far as the twenty-first concept of the present invention is concerned, the separator (2 ') as described above is in a hole in which the electrical connector (412) extends through a portion of the housing (384) of the separator (2'). Is arranged.

  A conventional ALFDEX® centrifuge, along with embodiments of the present invention, will now be described with reference to the accompanying drawings.

FIG. 1 is a perspective sectional view of a conventional ALFDEX (registered trademark) centrifuge. FIG. 2 is a cross-sectional side view of the separator shown in FIG. 1 in combination with a turbine vessel. FIG. 3 is a perspective cross-sectional view of an inlet / outlet nipple for use with the separator shown in FIG. 4 is a side cross-sectional view of the mold for the inlet / outlet nipple shown in FIG. FIG. 5 is a perspective view of the rotating body of the separator shown in FIG. FIG. 6 is a perspective sectional view of the rotating body shown in FIG. FIG. 7 is a perspective end view of the rotating body shown in FIG. 5, in which the upper rotating disk is shown detached from the rotating shaft of the rotating body, and the rotating shaft is a cross section. It is shown. FIG. 8 is a side cross-sectional view of the separator shown in FIG. 1, in which separated gas and oil flow paths are illustrated. FIG. 9 is a side cross-sectional view of the separator shown in FIG. 1, where a preferred oil flow path is illustrated. FIG. 10 is a side cross-sectional view of the separator shown in FIG. 1, in which an undesirable flow path for oil is illustrated. FIG. 11 is a perspective top view of the housing insert of the separator shown in FIG. FIG. 12 is a side perspective view of the housing insert shown in FIG. 11 in which a portion of the outer skirt of the housing insert has been removed and the undesired flow of oil droplets separated. It shows the road more clearly. FIG. 13 is a side perspective view of a first separator according to the present invention, in which the housing of the separator is shown in cross section and includes a rotating assembly and housing insert disposed within the housing. It is shown. FIG. 14 is an enlarged view of a region surrounded by a line A shown in FIG. FIG. 15 is a side perspective sectional view of the first embodiment of the present invention as shown in FIG. FIG. 16 is a side cross-sectional view of the inlet nipple connected to the inlet in the first embodiment. FIG. 17 is a perspective view of the inlet nipple and inlet of FIG. 16 separated from each other. 18 is a top perspective cross-sectional view of the first embodiment of FIG. 13, wherein the cross-section is parallel to the bearing plate of the first embodiment and passes through line 18-18 shown in FIG. Is taken on a flat surface. FIG. 19 is a side perspective sectional view of the second embodiment, wherein the second embodiment differs from the first embodiment in that a plastic material cover is provided on the upper end of the rotating assembly. Yes. FIG. 20 is a side perspective sectional view of the first embodiment shown in FIG. FIG. 21 is an upper perspective view of the upper rotating disk and the rotating shaft of the first embodiment shown in FIG. FIG. 22 is a velocity flow diagram showing the velocity of the inlet fluid with respect to the guide surface provided on the upper rotating disc shown in FIG. FIG. 23 is a lower perspective view of the upper rotating disk and the rotating shaft shown in FIG. FIG. 24 is a lower perspective view of one of the separator disks for slidable arrangement on the rotating shaft shown in FIGS. 21 and 23. FIG. 25 is a lower perspective view of the separator disk shown in FIG. 24 slidably disposed on the rotating shaft shown in FIGS. 21 and 23. FIG. 26 is a perspective view of a blower disk and a corresponding end plate disposed on the housing insert disposed on the bearing plate of the first embodiment shown in FIG. FIG. 27 is a side perspective view of a plurality of separator disks arranged on the rotating shafts of FIGS. 21 and 23, wherein the disks and rotating shafts are shown in FIG. Assembled with components. FIG. 28 is a top perspective view of the housing insert of the first embodiment shown in FIG. 13, wherein the housing insert is other than the oil splash guard positioned below the insert. It is shown separated from the components. FIG. 29 is a partial lower perspective view of the first embodiment shown in FIG. 13, and specifically shows the turbine vehicle assembly of the embodiment. 30 is a partial side cross-sectional perspective view of the turbine vehicle assembly shown in FIG. FIG. 31 is a partial side sectional perspective view of a turbine vehicle assembly instead of the turbine vehicle assembly shown in FIGS. 29 and 30. FIG. 32 is a lower perspective view of the turbine vehicle assembly shown in FIG. 33 is a side cross-sectional view of the first embodiment shown in FIG. 34 is an enlarged side cross-sectional view of the first embodiment shown in FIG. FIG. 35 is a side cross-sectional view of the electric motor driving apparatus shown in the above-mentioned drawing, in which the electric motor driving structure is shown used with the conventional separator of FIG. FIG. 36 is a schematic diagram showing the module types of the separator system shown in FIG. FIG. 37 is a diagram of the upper bearing unit of the first embodiment provided in the rotary welding jig. FIG. 38 is a diagram of the upper bearing unit of the first embodiment provided in the rotary welding jig. FIG. 39 is a side perspective view of the upper bearing unit provided in the rotary welding jig of FIGS. 37 and 38. FIG. 40 is a perspective view of the assembly shown in FIG. 39 disposed in the interior of the rotating body housing of the first embodiment prior to rotational welding of the upper bearing unit to the interior of the housing. FIG. 41 is a perspective view of the upper bearing unit attached to the inner surface of the housing shown in FIG. 40 by a rotary welding operation.

  With reference to FIGS. 1-12 of the accompanying drawings, a conventional ALFDEX® separator is shown, with specific main points left to the concept of a conventional separator improved by the present invention. It will be described from now.

  A number of views of a conventional ALFDEX® separator 2 being assembled are shown in FIGS. 1, 2, 8, 9 and 10 of the accompanying drawings. For those skilled in the art, a conventional separator 2 includes a rotating housing 4 that is generally cylindrical for receiving a number of internal components, the number of internal components being It is understood that it functions to separate oil from exhaust gas directed into the rotor housing 4.

  One end of the cylindrical housing 4 is provided with a rising annular shoulder 6 that defines a fluid inlet 8 to the separator 2. Thus, it is understood that the gas that is exhausted from the crankcase and from which oil separation is required enters the separator 2 via the fluid inlet 8.

  The hole 10 in the cylindrical wall of the rotator housing 4 is for passage of the cleaned gas from the interior of the rotator housing 4 into a further housing 12 corresponding to the valve unit 14 (see FIG. 1). Provide an exit. The valve unit 14 has a valve configuration for controlling the flow of the purified gas from the separator 2. Details of the operation of the valve unit 14 are not described here. However, as can be seen from FIG. 1, the outer shape of the rotor housing 4 matches the housing 12 of the valve unit 14 so that the two housings 4, 12 are suitable for receiving the internal components of the valve unit 14. It is specifically designed to be combined to define an internal space between the housings 4 and 12. The two housings 4 and 12 are fixed to each other by a conventional screw screw fixing member. It is therefore welcomed that the special valve unit housing 12 can be used only with the special rotor housing 4 having the required mating structure.

  Referring to FIG. 1, it can be seen that the housing 12 of the valve unit 14 is provided with a raised annular shoulder 18 that defines a fluid outlet through which the purified gas from the separator 2 passes. . The annular shoulder 18 provided on the valve unit housing 12 is substantially the same as the annular shoulder 6 provided on the rotating body housing 4. Thanks to their identity, the inlet and outlet shoulders 6, 18 can interchangeably accept inlet / outlet nipples having the same interface profile. One such nipple 22 having a 90 ° bend is shown as a cross-section in FIG. At one end of the nipple 22 is an annular collar 24 that defines an annular recess 26. The annular recess 26 has a square edge profile and a diameter that allows it to receive the housing annular shoulder 6,18 with which it abuts (and has a square edge). The interface of the shoulder 6 of the rotor housing 4 with the inlet nipple 28 can be seen with reference to FIG. 2 of the accompanying drawings. The nipple 28 shown in FIG. 2 has a different bending angle than the nipple 22 of FIG.

  The inlet / outlet nipples, against their corresponding housings 4, 12, press an annular washer 30 that pushes down on the shoulders 24 of the nipples 22, 28 when the screw threaded fastening member 32 is threaded into the two threaded holes 34. Used to secure them by clamping them on the housing shoulders 6, 18. Two bosses 34 rise from the associated housings 4, 12 and are arranged on either side of the annular shoulders 6, 18. An O-ring sealing member 36 is disposed between the recess 26 and the housing shoulders 6, 18 and is compressed and has inlet / outlet nipples and individual housings (see FIG. 2 for inlet nipples) To prevent unwanted leakage of fluid from the interface between the two.

  With further reference to the nipples 22, 28 shown in FIGS. 3 and 2, respectively, the second end of the nipple (distant from the end where the interface contour is provided) is on the second end of the nipple in use. To grip the hose being placed, teeth or serrated projections 38 are provided on its outer surface.

  Each of the fluid flow paths provided by the two nipples 22, 28 has a bend having an internal bend 40 that is substantially lacking in radius. In the prior art separator 2, angled nipples are manufactured using injection molding technology (for plastic nipples) and die casting technology (for aluminum nipples). ing. As readily understood from FIG. 4 (showing the mold of the nipple 22), the first and second inner mold parts 42, 44 in the direction indicated by the first and second arrows 46, 48. The mold portions 42 and 44 cannot be provided with a radius at the internal bend 40 so as to allow for removal.

  The aforementioned internal components stored by the rotor housing 4 will now be described in more detail with particular reference to FIG.

  First, the top bearing unit 50 is fixed to the inner surface of the rotor housing 4 immediately downstream of the fluid inlet 8. The top bearing unit 50 includes a caged bearing 52 that is trapped between an upper steel cap member 54 and a plastic material lower bearing seating member 56. The bearing unit 50 is manufactured by molding a lower bearing seating member 56 around an upper steel cap member 54 with a caged bearing 52 held between them. The configuration of the top bearing unit 50 is most clearly shown in FIG. 8, but it is also shown in FIGS. 2 and 9 in the context of a conventional separator 2.

  The bearing seating member 56 has a circular shape and abuts the cylindrical wall 60 of the rotating body housing 4 from the side in a state where the separator 2 is assembled (wraps the lower part of the cap member 54). It has a cylindrical wall 58 protruding downward. The abutment with the cylindrical wall 60 helps to ensure an accurate lateral positioning of the top bearing unit 50 with respect to the rotor housing 4. The second cylindrical wall 62 of the rotor housing 4 is located radially inward of the first cylindrical wall 60 to ensure accurate axial positioning of the top bearing unit 50 relative to the rotor housing 4. . The top bearing unit 50 is fixed to the rotating body housing 4 by three screw fixing members (not shown). In the configuration of the separator 2, the rotation center line of the top bearing unit 50 is concentric with the center line 64 of the rotor housing 4.

  Three partial circular slots 66 (only two are shown in FIG. 8) are provided in the top bearing unit 50 and are there (as indicated by arrows 68). Allow the flow of inlet fluid through the. However, as will be appreciated by those skilled in the art, the upper cap member 54 diverts the inlet fluid from the caged bearing 52 and the lower side of the uppermost portion of the cap member 54 is also ( In the caged bearing 52), during use, the lubricating oil mist that passes through the rotating shaft and moves into the top bearing unit 50 is deflected.

  The remaining internal components of the separator 2 are assembled separately with respect to the rotor housing 4 and are therefore arranged in the housing 4 as an integral assembly. The integral assembly includes a first group of components that remain stationary relative to the rotator housing 4 during use of the separator 2 and the rotator housing 4 (and valve unit) during use of the separator 2. And a second group of components that rotate about a center line 64 relative to both the housing 12) and the first group of components.

  The first group of components comprises an annular bearing plate 70 and a dish-shaped member 72, known as a housing insert. The housing insert 72 functions in combination with the bearing plate 70 to isolate the separated oil from the cleaned gas before the separated oil and cleaned gas exits the rotor housing 4. . The bearing plate 70 is made of steel and the housing insert 72 is made of a plastic material. The bearing plate 70 and the housing insert 72 have three screw screw fixing members 74 (only one is shown in FIG. 1 of the accompanying drawings) to be screwed with a boss 76 protruding downward from the lower side of the housing insert 72. Are fixed to each other. This first group of components will be discussed in more detail later in this description.

  The second group of components forms a rotating assembly and a plurality of individual separating disks 82, end plates 86 that together form a stack 84 of rotating shafts 78, upper rotating disks 80, and separating disks 82. And a combined fan and turbine unit 88. This second group of components are secured together to prevent their rotation relative to each other. The second group of components is, however, rotatably provided in the first group of components by a bottom bearing unit 90 (see in particular FIG. 10).

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

  The rotating shaft 87 is formed of a metallic material and has an annular cross section to provide a fluid flow path 92 extending longitudinally along its entire length. During use of the separator 2, this flow path 92 allows oil mist to move upwards from the turbine vessel into the top bearing unit 50 via the rotating shaft to lubricate the bearings of the unit 50. A restraining element 93 in the form of an annular disc (with a cylindrical wall rising from its radially outer peripheral edge) is on the inner shoulder facing above the fluid flow path at the upper end of the rotating shaft 78 Has been placed. The restraining element 93 functions to reduce the flow area through the rotating shaft 78 at the outlet from the rotating shaft 78 into the top bearing unit 50 (thus providing a nozzle).

  A number of recesses and shoulders are provided on the exterior of the rotating shaft 78 to accept a circlip that helps the remaining components be in the correct axial position on the rotating shaft 78. One such circlip 94 is clearly shown in FIG. 6 as providing an upward facing shoulder against which a washer 95 abuts. The circumferential recess in which the snap ring 94 is placed is wide enough to allow the snap ring 94 to move axially along the axis of rotation 78 (within the recess) (ie, , Dimension of the recess in the axial direction). This allows the spring 96 to apply an axial force to the bottom bearing unit 90.

  Other recesses are provided on the outer surface of the rotating shaft 78 to place and maintain the components on the shaft 78. Each of the upper rotating disc 80, the separating disc 82, and the end plate 86 extends radially inward therefrom to a hub element disposed about the rotational axis 78 in use. It has a truncated frustoconical part (defining the upper truncated frustoconical surface 102) with a spoke member.

  The spoke members of the upper rotating disc 80 and the separating disc 82 have an open space between them to allow fluid flow therethrough axially along the axis of rotation 78, and the spokes of the end plate 86. The members are joined together at their lower surfaces to prevent axial flow of fluid along the axis of rotation 78, either passing up the end plate 86 or passing down the end plate 86.

  The truncated frustoconical shapes of the upper rotating disc 80 and the end plate 86 are substantially the same as those of the separating disc 82, and the upper rotating disc 80 and the end plate 86 are stacked with the separating disc 82. In this case, the upper rotating disk 80 is disposed on the top of the separating disk stack 84, and the end plate 86 is disposed on the bottom of the separating disk stack 84. Furthermore, it will be appreciated by those skilled in the art that the separation disc 82 is relatively thin to allow a large number of discs to be provided in a relatively short stack 84, and the upper rotating disc 80 and end plate 86 are circular. Provide rigidity to either end of the plate stack 84, thereby allowing the upper disc 80 and end plate 86 to apply a compressive axial force evenly to the frustoconical portion of the separating disc. It is much thicker than the separation disk 82. More specifically, the compression force is generated by a helical compression spring 96 that pushes the lower side of the hub 98 of the end plate 86 upward.

  With respect to compression of the disk stack 84 between the upper rotating disk 80 and the end plate 86, the adjacent separation disks 82 in the stack 84 are allowed to allow fluid flow through the separator 2. It will be appreciated by those skilled in the art that a space must be left between them. This space of the separation disk 82 is provided by a plurality of ribs 100 (known as caulk) provided on the upper surface of the truncated frustoconical portion of each separation disk 82. . Individual caulks 100 extend from the radially inner edge 104 of the upper surface 102 to the radially outer edge 106 of the surface. Caulk 100 rises on the upper surface 102 and abuts the lower surface of the adjacent disk in the assembled stack 84 of separation disks 82. As will be appreciated by those skilled in the art, the individual separation discs 82 can be positioned on the rotation axis 78 in one of only six possible angular positions relative to the rotation axis 78, and The positioning of the caulk 100 on the upper surface 102 means that the disks 82 must be aligned with each other when placed in any of these six positions. As a result, the compressive force applied to the disk stack 84 by the end plates 86 is transmitted through the stack 84 by the aligned caulk 100 without closing the space between the separating disks 82.

  It will be appreciated by those skilled in the art that with respect to the compression force applied to the separation disk stack 84, this force is generated by the helical compression spring 96 and applied to the end plate hub 98. Due to the rigidity of the end plate 86, the compressive force is transmitted from the hub 98 to the truncated frustoconical portion 108 of the end plate 86 through the plurality of radially extending spokes 110 of the end plate 86. The compressive force is then transmitted through the truncated frustoconical portion 108 to the disk stack 84 and through the stack 84 (through the caulk 100) upwards of the upper rotating disk 80. It is transmitted to the truncated truncated cone part 112. The compressive force is transmitted to the hub 114 of the upper rotating disc 80 through six radially extending spokes 116 from the truncated frustoconical portion 112 of the hub 114 of the upper rotating disc 80. The compressive force is transmitted from the truncated truncated cone portion 112 to the hub 114 due to the rigidity of the upper rotating disk 80. The axial movement of the upper rotating disc 80 upward along the rotating shaft 78 due to the reaction to the compressive force is caused by the arrangement of the upper rotating disc hub 114 in the circumferential recess 118 on the outer surface of the rotating shaft 78 (particularly FIG. (See 6). The frictional force between the hub 114 and the outer surface of the rotating shaft 78 prevents relative rotation between them.

  It can be seen in particular from FIGS. 6 and 8 that the hub 114 of the upper rotating disc 80 extends axially downwards to the point directly above the end plate hub 98 along the axis of rotation 78. More particularly, the hub 114 extends along the entire depth of the separation disk stack 84 and thereby separates the hub 120 of the individual separation disk 82 from the axis of rotation 78 (see FIG. 7). The hub 120 of each individual disc 82 has a hexagonal shape defining a hexagonal hole through which the rotating shaft 78 and the upper rotating disc hub 114 extend. The rotational movement of the separating disk hub 120 relative to the upper rotating disk hub 114 (and thus relative to the rotating shaft 78) is provided axially along the length of the upper rotating disk hub 114 and is separated from the separating disk hub. Blocked by six splines 122 extending radially into the six corners of the hexagonal hole defined by 120. This arrangement of splines 122 prevents lateral movement and rotational movement of the separating disc hub 120 relative to the rotating shaft 78.

  The separation disk hub 120 of each separation disk 82 is connected to the truncated frustoconical portion 124 of each separation disk 82 by twelve radially extending spokes 126. The spokes 126 (and indeed the remainder of the corresponding separating disc 82) are made of a plastic material that is relatively thin and elastically bendable. However, the spokes 126 can nevertheless resist the lateral and rotational forces to which they are exposed without deformation. It will be appreciated by those skilled in the art that the compressive force generated by the helical spring 96 is transmitted through the separating disk stack 84 via the caulk 100 rather than by the separating disk spokes 126.

  The relative arrangement of the hexagonal hubs 120 and splines 122 of the individual separating disks 82 is as described above, with the individual separating disks 82 being disposed on the rotating shaft 78 in one of only six angular positions. Ensure that it is possible. However, the polar or angular position of the caulk 100 of the separation disk 82 is the same regardless of the six angular positions used, and therefore the separation disk stack 84 is There is no possibility that the caulk 100 of the adjacent separation disk 82 is assembled on the rotating shaft 78 in a state where it is misaligned.

  For purposes of clarity, certain figures in the accompanying drawings show disk stacking with the presence of a reduced number of separating disks. With particular reference to the prior art separator 2, FIGS. 1, 2, 8, 9 and 10 are thus simplified.

  As shown in FIG. 5, the second circumferential recess 128 is provided at the upper end of the rotating shaft 78 at a position above the first recess 118. The second circumferential recess 128 receives the second helical spring 130. The location of the second recess is such that, in the assembled conventional separator 2, the lower end of the second spring 130 is separated from the hub 114 of the upper rotating disc 80 (see FIG. 6), and the second It appears that the upwardly facing shoulder formed by the recess 128 prevents the downward axial movement along the rotational axis 78. Furthermore, in the assembled separator 2, the vertical bearing (with the upper end of the rotary shaft 78 kept away from the cap member 54 of the top bearing unit 50—see in particular FIG. 8) (Caged bearing) 52 ridges abut against the second spring 130 and compress downward. The second spring 130 applies a load to the top bearing unit 50 and thereby reduces vibration and corresponding wear on the top bearing unit 50.

  Most of the combined fan and turbine 88 of the second group of internal components are shown assembled in FIG. 6 of the accompanying drawings. Before the fan / turbine unit 88 is provided at the lower end of the rotary shaft 78, the lower end of the shaft 78 is a central circular hole provided in the bearing plate 70 and the housing insert 72 of the first group of internal components. Is placed through. By doing so, the lower end of the rotating shaft 78 is also extended through the bottom bearing unit 90 which is fixed in the central hole of the bearing plate 70 (see in particular FIGS. 8 and 10).

  The combined fan and turbine 88 are fixed to the lower end of the rotating shaft 78 projecting downward from the lower side of the bearing plate 70. The fan / turbine unit 88 contacts the upwardly facing surface of the second snap ring 132 and the second snap ring 132 (held in a third circumferential recess in the shaft 78). The second washer 133 in contact with the rotating shaft 78 is held at a predetermined position on the lower end. The axial positioning of the fan / turbine unit 88 on the rotating shaft 88 is determined by a second circlip 132 so that the upper surface of the unit 88 is pushed against the deflector washer 139. As a result, the deflector washer 139 is then pushed into contact with the bottom bearing unit 90. In the assembled separator 2, the inner race of the bottom bearing unit 90 abuts against the first snap ring 94, and this snap ring 94 is resisted against the bias of the first compression spring 96. Press upwards. The pressing of the inner race, deflector washer 139, and fan / turbine unit 88 against the second circlip 132 holds these components in a fixed rotational position relative to the rotational shaft 78.

  The rotating assembly of separator 2 is rotated by the hydraulic impulse turbine in the direction indicated by arrow 134 (see FIG. 1). The fan / turbine unit 88 includes a Pelton wheel 136 having a plurality of buckets 138 evenly spaced along its circumferential direction. In use of the separator 2, oil injection is directed from the nozzle (not shown) in the turbine vessel 178 toward the periphery of the Pelton wheel 136. More particularly, the jet is directed along a tangent to a circle passing through a plurality of buckets 138, so that the jet enters a bucket that is aligned with its surface. The jet flows along the surface following the internal contour of the bucket and is then reversed by the contour to flow along a further surface and then discharged from the bucket. As a result, the injection rotates the wheel 136.

  A fan having a plurality of blades 140 is also formed integrally with the wheel 136. The wing 140 is disposed on the vehicle 136 in close proximity to the lower side of the bearing plate 70. The plurality of blades 140 are also at substantially the same axial position as the bottom bearing unit 90 along the rotational axis 78. The fan blades 140 extend radially outward from near the bottom bearing unit 90. It will be appreciated by those skilled in the art that the fan blades 140 rotate about the centerline 64 when the turbine wheel 136 rotates. By so moving, the fan blades 140 efficiently throw fluid from the area between the wheel 136 and the underside of the bearing plate 70, thereby reducing the fluid pressure in the area of the bottom bearing 90, and From the position above the bearing plate 70, the separated oil is drawn downward through the bottom bearing unit and into the turbine vessel 178 below the bearing plate 70.

  For ease of manufacture, the wheel 136 is formed by upper and lower portions 142, 144 and is pushed against each other at line 146 as shown in FIG. 8 of the accompanying drawings.

  For the first group of internal components, the bearing plate 70 is made of steel and has a circular shape with a diameter substantially equal to the diameter of the rotor housing 4. This relative arrangement allows the bearing plate 70 to be placed on the shoulder 148 facing downward below the lower end of the rotor housing 4. In this way, the lower opening end of the rotating body housing 4 is closed by the bearing plate 70. The bearing plate 70 is also provided with a central circular hole that is concentric with the rotor housing 4 in the assembled separator 2. In other words, in the assembled separator 2, the circular center hole of the bearing plate 70 is centered on the center line 64 of the rotating body housing 4. Furthermore, as will become particularly apparent from FIG. 1 of the accompanying drawings, the bottom bearing unit 90 is received in the central hole of the bearing plate 70. The outermost portion of the bottom bearing unit 90 in the radial direction is fixed to the bearing plate 70. The innermost portion in the radial direction of the bottom bearing unit 90 is disposed adjacent to the rotating shaft 78, but is not fixed thereto. As described above, the first group of internal components also includes a housing insert 72 that is secured to the bearing plate 70. The housing insert 72 functions to isolate clean gas from the oil separated therefrom and to provide an outlet 150 for clean gas, which is connected to the outlet hole 10 of the rotor housing 4. (See especially Figure 1). The housing insert 72 is provided as an integral molding of a plastic material. However, in the description of the housing insert 72 below, the insert is an outer cylindrical wall / skirt portion 152, a groove portion 154, a truncated frustoconical portion 156, and an outlet defining the insert outlet 150. Consider that it comprises four parts 158.

  The cylindrical skirt portion 152 of the housing insert 72 has an outermost outer diameter that is substantially equal to the diameter of the inner wall portion of the rotating housing 4 that abuts the skirt portion 152. A circumferential recess 159 (see FIG. 12) is provided in the outer surface of the skirt portion 152 to receive the O-ring seal 160, the O-ring seal 160 being assembled. In machine 2, a fluid seal between the housing insert 72 and the rotator housing 4 is ensured.

  The lower end of the cylindrical skirt portion 152 abuts the upper side of the bearing plate 70 and is provided with a circumferential recess 162 (see FIG. 12) for receiving the second O-ring seal 164. It will be appreciated that the second O-ring seal 164 ensures a fluid seal between the housing insert 72 and the bearing plate 70.

  A second cylindrical wall located radially inward of and disposed concentrically with the outer skirt portion 152 is connected to the outer skirt portion 152 at its lower end to form a groove portion 154. Yes. The groove portion 154, together with the outer skirt portion 152, forms an annular groove (or recess) 166 that extends along the inner cylindrical wall of the rotator housing 4. The groove 166 has a U-shaped cross section and collects the separated oil drops thrown from the separation disk 82 during use of the separator 2 and under the action of gravity (and here) As described in more detail below, under the action of a downward spiraling gas flow). The groove portion 154 passes oil collected in the groove 166 therethrough into a region enclosed by the lower side of the housing insert 72 and the upper side of the bearing plate 70 during use of the separator 2. There are four discharge holes 168 (see especially FIG. 11) that can flow.

  The third portion 156 of the housing insert 72 has a truncated frustoconical shape and is suspended from the groove portion 154. The truncated truncated cone part 156 is provided with a central circular hole having a center line concentric with the center line 64 of the rotating body housing 4 in the assembled separator 2. An elongated recess 170 (see FIG. 11) is provided in the upper surface of the truncated frustoconical portion 156. This recess 170 defines a fluid passage for clean gas coupled to the outlet portion 158 of the housing insert 72. The flow path provided by the recess 170 begins with a step 172 directed downward from the upper surface of the truncated frustoconical portion 156 at its upstream end. The sidewalls 174, 176 of the recess 170 increase in height in the downstream direction as the fluid passage proceeds outward from the center of the housing insert 72. As is apparent from the top surface of the housing insert 72 provided by FIG. 11, the recess 170 provides a straight fluid passage having a length approximately equal to half the diameter of the housing insert 72. Yes.

  The outlet portion 158 of the housing insert 72 is provided in the form of a generally cylindrical tube that extends across the groove 166 between the hole in the outer skirt portion 152 and the groove portion 154.

  A view of the separator 2 secured to the turbine vessel 178 is shown in FIG. The separator 2 is fixed to the turbine vessel 178 by three screw fixing members 180 that pass through one of three bosses integrated with the lower end of the rotating body housing 4. Only one securing member 180 and boss 182 are shown in the cross-sectional side view of FIG. The bearing plate 70 (and thus all of the components of the first and second groups) faced downward with the turbine vessel 178 pushing the bearing plate 70 when the rotor housing 4 and the turbine vessel 178 are secured together. Those skilled in the art will appreciate from FIG. 2 that the abutment against the shoulder 148 holds it in the desired position relative to the rotator housing 4. The bearing plate 70 is essentially sandwiched between the rotating body housing 4 and the turbine vessel 178 by a screw fixing member 180. The second helical compression spring 130 is compressed by the top bearing unit 50 as the screw fixing member 180 is tightened and the bearing plate 70 is brought into contact with the shoulder 148 as a result.

  During operation of the separator 2, a nozzle (not shown) in the turbine vessel 178 directs the injection of oil onto the turbine wheel 136, indicating the turbine vehicle as indicated previously with reference to FIG. Rotate in the direction pointed out by This rotation of the turbine wheel drives the overall rotation of the rotating assembly in the direction of arrow 134 about the centerline 64 of the rotating body housing 4. In other words, the rotating shaft 78, the upper rotating disc 80, the stack 84 of separating discs 82, the end plates 86, and the combined fan and turbine unit 88 (ie, collectively referred to herein as a rotating assembly). However, the rotating body 4 rotates together with the housing 4 and the bearing plate 70, the housing insert 72, and the turbine vessel 178 as an integral assembly.

  Gas discharged from the engine crankcase and requiring processing by the separator 2 is introduced into the separator 2 via a fluid inlet 8 located at the top of the rotor housing 4. As indicated by arrow 68 in FIG. 8, the introduced gas enters the rotor housing 4 in a direction parallel to and along the center line 64 and passes through the six spokes 116 of the upper rotating disc 80. Before flowing through the three elongated holes 66 in the top bearing unit 50. The rotational movement of the six spokes also results in the lateral movement of the fluid located between the spokes, where the fluid moves tangentially from the circular path of the spoke 116 and rotates. It is efficiently thrown outward toward the cylindrical wall of the body housing 4. In essence, the six spokes 116 impart cylindrical movement on the incoming gas.

  As the incoming gas flows downwardly through the upper rotating disc 80 and the spokes 116, 126 of the separating disc 82, the gas is between adjacent separating discs 82 as indicated by arrows 184 in FIG. Is moved laterally toward the cylindrical wall of the rotor housing 4 through the space. The caulk 100, along with the frictional force applied by the separating disc 82, imparts lateral movement over the fluid disposed in the disc stack 84, and the fluid is in the rotor housing 4. The result is that it moves outward toward the cylindrical wall. This movement of the fluid produced by the rotation of the disk stack 84 is the first mechanism by which the fluid is drawn into the separator 2.

  It will be appreciated by those skilled in the art that the oil drops 186 will collect together to form larger drops around the disk stack 84. In this regard, the capillary force acting on the small oil droplets (due to the small space between adjacent separating disks 82) prevents the droplets from being thrown out of the disk stack 84. However, as much oil moves across the separation disk, the droplets are gathered together around the periphery and have sufficient mass (and corresponding “centrifugal” force) to overcome the capillary force. Form larger drops. The oil is then thrown onto the cylindrical wall of the rotator housing 4. Once received by the cylindrical wall, the oil drop 186 moves downward under the action of gravity and the gas flow through the separator 2 enters the annular groove 166. The outermost circumferential edge of the separator stack 84 allows the oil droplets to move downward into the groove 166 without being obstructed by the separation disk 82. It is far enough inward from the cylindrical wall. O-ring sealing member 160 has the potential consequence that oil droplets contaminate clean gas flowing through outlet 150 of housing insert 72 (as best understood by referring to FIG. 1). Rather than between the housing insert 72 and the rotator housing 4, it is ensured that it flows into the groove 166.

  The oil droplets 186 collected in the groove 166 are discharged from there through the four discharge holes 168. This discharge operation is assisted by the fluid pressure gradient in the rotor housing 4 and the turbine vessel 178. More specifically, due to the rotational movement of the rotating assembly, the fluid pressure in the rotating body housing 4 is greater than that in the region between the lower side of the housing insert 72 and the upper side of the bearing plate 70. It is understood by those skilled in the art that the circumference at 84 is greater. The result is a downward purified gas flow through the exhaust holes 168. This fluid flow allows the separated oil droplets to pass down the discharge holes 168 along the annular groove 166 onto the lower bearing plate 70. This gas fluid flow is indicated by arrows 188 (see especially FIG. 8). The gas fluid flow traverses the upper surface of the bearing plate 70 and moves radially inward toward the central circular hole in the housing insert 72. This flow across the bearing plate 70 directs the separated oil droplets across the bearing plate 70 to the bottom bearing unit 90 through which the oil droplets pass. The combined fan and rotating fan blades 140 of the turbine unit 88 lower the static pressure in the turbine vessel 178 in the region of the bottom bearing unit 90. This in turn helps to suck the oil droplets through the bottom bearing unit 90. However, even if the pressure in the turbine housing is greater than the pressure in the rotor housing, in use, the baffle washer 139 that rotates with the turbine unit relative to the bearing plate 70 causes the oil droplets to cause the bottom bearing unit 90 to move. Basic means to be drawn through are provided to pump oil from the rotor housing 4. The fan blades 140 then throw the drops outward into the turbine vessel 178 from which they can be returned to the engine crankcase. During this time, the gasified fluid flowing across the bearing plate 70 is drawn upward through the central hole of the insert housing 72 and is rotated by the housing insert outlet 150 and the rotator housing outlet 10. Exit housing 4.

  An alternative path between the end plate 86 and the upper portion of the groove portion 154 (without flowing into the groove 166), as well as flowing through the exhaust holes 168. The flow to the outlets 150, 10 through is also preferably with reference to the accompanying drawings. This alternative path is indicated by arrow 190.

  The oil flow through the bottom bearing unit 90 has an effective lubricating effect on the bearing unit. The top bearing unit 50 is similarly lubricated by an oil mist that naturally occurs in the turbine vessel 178 and travels upwardly through the longitudinal flow path 92 extending through the rotating shaft 78 to the top bearing unit 50. Is done.

  Although the conventional separator 2 has been proven to work effectively, there are a number of problems associated with separators that are addressed by the improvements found in the improved separators described below. is there. These problems can be considered in three broad categories.

  First, the fluid passage through the separator 2 causes a pressure loss that adversely affects the flow rate of the separator and, consequently, the dimensions of the engine in which the separator can be used. The first section of the problem corresponding to conventional ALFDEX ™ separators can therefore be considered as related to the pressure loss in the fluid flow path.

  Second, the structure of conventional separators can, under certain circumstances, cause the cleaned gas to become contaminated before leaving the separator. Thus, the second section of the problem corresponding to conventional separators can be considered as related to undesired oil contamination of the cleaned gas.

  Third, certain manufacturing techniques and structural features associated with conventional separators can lead to assembly difficulties and / or reliability problems. Thus, the third category of problems associated with conventional separators can be considered as related to the manufacture and reliability of the separator.

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

  There are many places where relatively high pressure losses are encountered with respect to the fluid flow path through the separator 2. First, the bend internal bend 40 in the inlet / outlet nipples 22, 28 is sharp so as to cause fluid separation from the inner surface of the nipple in the downstream region immediately after the bend 40. This separation is manifest as a recirculating fluid flow (or vortex), which in turn results in energy / pressure loss. However, as described above in connection with FIG. 4 in the accompanying drawings, providing a large radius over the internal bend is questionable when manufacturing inlet / outlet nipples by injection molding or die casting techniques. There is. As a result, the conventional separator 2 experiences pressure loss at the nipple both at the inflow of fluid to the rotor housing 4 and at the discharge from the valve unit housing 12.

  The inventor has also identified the six spokes 116 of the upper rotating disc 80 as further causing undesirable pressure losses. In particular, each of the spokes 116 has a rectangular cross section, and the exhausted gas flows in when the upper rotating disc 80 is rotating in the direction of arrow 134 (see FIG. 5). Providing a sharp upper trailing edge for axial flow can be seen in particular from FIGS. It has been found that the shape of the spoke 116, particularly the sharp trailing edge 192 of the spoke, causes fluid separation and undesirable pressure loss.

  The inventor has also discovered that the special configuration of the housing insert 72 causes undesirable pressure losses. In particular, during use of the separator 2, the gas being cleaned is accompanied by rotational movement about the center line 64 as indicated by arrow 194 in FIG. Flows downward on portion 156. This flow of gas being cleaned flows over the truncated frustoconical portion 156 and then flows downwardly in a spiral fashion along the inner surface of the cylindrical side wall of the rotor housing 4. Therefore, the gas being cleaned will flow from all points along the circumferential periphery of the housing insert 72 to the region between the truncated frustoconical portion 156 and the upper end plate 86 (above one particular position). It is understood that it enters (rather than entering the area). The flow path across the frustoconical portion 156 thus has a spiral pattern that can cause undesirable pressure / energy losses. Furthermore, the step 172 of the recess 170 and the walls 174, 176 provided in the truncated frustoconical portion 156 cause additional areas of fluid separation and corresponding undesirable pressure losses.

  Regarding the second category of problems related to oil contamination, the inventor has pointed out a number of features of the conventional separator 2 that increase the tendency of clean air to be contaminated under certain conditions. . First, as previously mentioned, the oil stream that has been cleaned down through the rotor housing 4 partially enters the groove 166 and is separated through the exhaust hole 168. There is a tendency to pull drops. If the flow rate of air being cleaned is insufficiently high to handle a particular level of oil contamination, then the oil droplets collected in the groove 166 will cause the groove portion 154 of the housing insert 72 to flow. It can then be climbed and then flows over the truncated frustoconical portion 156 of the housing insert 72 (see FIG. 10). Once the oil drop enters the area between the frustoconical portion 156 and the end plate 86, the oil drop necessarily leaves the separator 2 and contaminates the gas being cleaned. The climbing of the oil droplets from the groove 166 can result in a low flow rate of the cleaned gas that allows an undesirably high amount of oil to collect in the groove 166. The presence of the cleaning gas swirling upward in the groove 166 also tends to draw oil drops upward onto the truncated frustoconical portion 156 of the housing insert 72. However, an important feature of the conventional separator 2 that allows oil drops to climb up out of the groove 166 is the tubular outlet portion 158 (see FIG. 12). Regardless of which side of the outlet portion 158 the outlet hole 168 is located, the oil drop in the groove 166 follows a circular path along the bottom of the groove 166 and if the oil drop is discharged upstream just before the outlet portion 158 If it did not flow through the hole 168, the oil droplet would flow in the passage indicated by arrow 196 (see FIG. 12) and over the outlet portion 158 upwardly the truncated frustoconical portion of the housing insert 72. It can be seen from FIG. 12 of the accompanying drawings that it flows over 156.

  The inventor also describes that the oil drops that have been separated flow up through the central hole of the housing insert 72 onto the frustoconical portion 156 and thereby contaminate the gas being cleaned. I have discovered that. This undesired flow of separated oil is caused by the flow of cleaned gas passing through the exhaust hole 168 and upward through the central hole of the housing insert 172 (as pointed out by arrow 188 in FIG. 8). It tends to occur when the flow rate is relatively high. The high flow rate of the gas being cleaned results in oil droplets being separated rather than allowing the oil droplets being separated to be pulled down through the bottom bearing unit 90 by the action of gravity and baffle washers 139. Will be understood by those skilled in the art to result in being transported upward through the central hole of the housing insert 72.

  The inventor also introduces excess oil into the separation disk stack 84 via a longitudinal flow path 92 through the axis of rotation 78, as indicated by the arrow 198 shown in FIG. I have discovered that I can do it. During normal operating conditions, the jet of oil driving the turbine wheel 136 impinges on the vehicle and causes fine oil droplets to be cut. This mist of oil is moved up to the top bearing unit 50 and then down through the stack of separation discs 82. Normally, the amount of oil moved in this way is sufficient to lubricate the top bearing unit 50 and is substantially easily separated from the incoming gas flow by the separating disk stack 84. However, in some situations, the amount of oil moved through the rotating shaft 78 causes the oil to overflow from the groove 166 or onto the truncated frustoconical portion 156 of the housing insert 72 and then clean. The resulting flow into the gas outlet 10 can be increased. This can occur, for example, when the separator 2 is tilted or when the lower end of the rotating shaft 78 is directly exposed to the surface of the oil sump held in the turbine vessel 178.

  Regarding the third category of problems related to difficulties with manufacturing and reliability, the inventor has pointed out the following problems with the conventional separator 2.

  First, with respect to manufacturing the separator 2, the inventor has spent time using the threaded fastening member 32 to secure the inlet / outlet nipple to the rotor housing 4 and valve unit housing 12, and It has been discovered that an O-ring sealing member 36 is required.

  The length of time spent manufacturing the conventional separator 2 is also such that the top bearing unit 50 and the bottom bearing unit 90 are in such a way that both bearing units 50, 90 can rotate about the same center line 64. Affected by the need to be axially aligned. In particular, when the rotator housing 4 is formed from a plastic material by an injection molding process, the inventor has discovered that the rotator housing 4 tends to flex during cooling. As a result of this deflection, the position of the first cylindrical wall 60 of the rotating body housing 4 (with the top bearing unit 50 disposed laterally) is intended for the lower end of the rotating body housing 4. There is a tendency to be located at different lateral positions. As a result, the bearing plate 70 (and thus the bottom bearing unit 90) can be laterally separated from its intended position. This problem can be alleviated by allowing the rotator housing 4 to be cooled over a relatively long period following the injection molding process. This long cooling period reduces the deflection of the rotor housing 4, but increases the production time.

  A further problem corresponding to the assembly of the separator 2 relates to the boundary between the various components, such as between the rotor housing 4 and the valve unit housing 12. More specifically, if the separator 2 is provided with a different valve unit 14 (or no valve unit) than originally intended, a new valve unit (or other unit in which the valve unit is not used) is provided. In order to ensure an exact interface with the pipe system), a different rotor housing 4 must also be used. This excessively increases cost and assembly time. Furthermore, the asymmetry of the rotor housing 4 (caused by the mold shape provided on the housing 4 to bound the valve unit housing 12) results in the housing 4 being bent during manufacture. And then results in problems during assembly (eg, problems related to misalignment of components).

  It has also been pointed out by the inventor that the large O-ring sealing member 160 provided on the housing insert 72 may be damaged. More specifically, the O-ring sealing member is required to seal against two large diameter mating surfaces, one surface is provided on the housing insert 72, and one surface is The rotating body housing 4 is provided on a cylindrical wall. Both the rotator housing 4 and the housing insert 72 have relatively large manufacturing tolerances that can result in the O-ring sealing member 160 not accurately sealing the two components. Furthermore, since the two components are manufactured from plastic material using injection molding techniques, the individual molds (and in particular the molds of the rotor housing 4) are subject to deflection following the injection molding process. This can further result in the O-ring sealing member 160 failing to accurately seal the two components 4,72. If the O-ring sealing member 160 fails, then the separated oil is in the region 200 between the outer cylindrical skirt portion 152 of the housing insert 72 and the cylindrical wall of the rotating housing 4. It is understood that leaks. Oil leaking into this region 200 will eventually pass into the outlet 150 of the housing insert 72 and contaminate the gas being cleaned. If the O-ring sealing member 160 fails near the outlet 150, then the separated oil leaks through the O-ring sealing member 160 and enters the outlet 150 directly. This sealing problem can be either (i) taking action to reduce the deflection effect (by increasing the cooling time following the injection molding process) or (ii) the leaking component being replaced following product testing, Manufacturing time can be increased.

  Further, a molding burr disposed in the recess 159 that receives the O-ring sealing member 160 can result in the o-ring sealing member being spoiled.

  The inventor has also pointed out a reliability problem corresponding to a structure for disposing the separating disk 82 in a predetermined angular arrangement with respect to the rotating shaft 78. As described above in connection with FIG. 7 of the accompanying drawings, the separation disc 82 is engaged with a hexagonal hole in the hub 120 or individual separation disc 82 (fixed to the rotating shaft 78). ) The rotation is prevented with respect to the rotation shaft 78 by six splines. However, vibrations (such as engine vibrations) that the separator is typically exposed to during use can cause wear at the interface between the spline 122 and the hexagonal hole in the hub 120. This wear can result in a large relative rotational movement between the separating disc 82 and the rotating shaft 78. In fact, the inventor has found that the adjacent separating disks 82 can rotate relative to each other to the extent that the alignment of the caulk 100 is broken and the gap between the adjacent separating disks 82 is narrowed. discovered. If this occurs in a very large number of discs 82, then the depth of the separation disc stack 84 is reduced to such an extent that the hub 98 of the end plate 86 is pressed against the upper rotating disc hub 114 by the compression spring 96. I can do it. The end plates 86 are then unable to transmit any further compressive force to the separation disk stack 84 and, as a result, the individual separation disks 82 (with rotation relative to the rotation axis 78) to the rotation axis 78. It moves freely up and down along the axis. This movement is highly undesirable and greatly reduces the separation performance of the rotating disk stack 84.

  Further reliability issues pointed out by the inventor include: (i) between the rotary shaft 78 and the top / bottom bearing units 50, 90, and (ii) between the rotary shaft 78 and the first compression spring 96. It is related to fretting corrosion at the interface. It is understood by those skilled in the art that fretting corrosion occurs when relative movement between components is possible (eg, due to a relatively loose fit between the components). . A rotating shaft 78 extends through the top and bottom bearing units 50, 90 and the first compression spring 96 with a relatively loose fit. This allows an axial preload to be applied to the top and bottom bearing units 50, 90 by the first and second compression springs 96, 130. In particular, it can be seen from the drawings that the first compression spring 96 applies an axial force to the bottom bearing unit 90 and the second compression spring 130 applies an axial force to the top bearing unit 130. The loose fit of the rotating shaft 78 with the top and bottom bearing units 50, 90 and the first compression spring 96 allows movement with vibration between these components. This in turn causes fretting corrosion on the component. The relative motion between the components can also allow hard particles to enter between the components, further promoting wear and leading to reliability problems.

  An improved separator developed by the inventor addressing the above problems will now be described with reference to FIGS.

  The improved separator developed by the inventor has many components that are similar or the same as the conventional separator 2 in terms of the functions they perform and their overall configuration. This is immediately understood by those skilled in the art. Such components are described below in terms of a separator that has been improved by using the same reference numerals as described above for the conventional separator 2. For example, referring to FIG. 13 of the accompanying drawings, the improved separator 2 ′ shown in this figure corresponds to the rotating body housing 4 of the conventional separator 2 and is generally a cylinder that achieves the same function. The person skilled in the art understands that the rotor housing 4 'is shaped. Such structural and functional differences between corresponding components will become apparent to those skilled in the art from the accompanying drawings, however, these differ from conventional separators 2 or conventional separators 2. It is generally discussed in detail when it is important in addressing problems with the manufacturing process or providing improvements.

  The improved separator 2 ′ comprises a substantially cylindrical rotor housing 4 ′ and a number of internal components that function to separate the oil from the exhausted gas directed into the rotor housing 4 ′. To be understood by those skilled in the art. As described below, some of the internal components are located within the rotor housing 4 'and other internal components (eg, combined fan and turbine unit) are external to the rotor housing 4'. However, it is disposed in another housing (eg, a turbine vessel).

  The upper end of the cylindrical housing 4 'is provided with a rising annular shoulder 6' defining a fluid inlet 8 'for the improved separator 2'. Gas discharged from the crankcase and requiring separation of oil therefrom enters the separator 2 'via the fluid inlet 8'.

  The hole 10 'in the cylindrical wall 201 of the rotator housing 4' passes through the cleaned gas through the interior of the rotator housing 4 'into another housing 12' of the valve unit 14 '. Provide an exit (see particularly FIGS. 13, 14 and 15). The exit hole 10 'passes through and is surrounded by a cylindrical boss 202 which itself extends from the outer surface of the rotating housing 4'.

  The valve unit 14 'is provided with a valve structure for controlling the flow of purified gas from the separator 2'. Regarding the description above the conventional separator 2, details of the operation of the valve unit 14 'are not described here. Those skilled in the art, however, are familiar with the functional operation of a valve unit for use with an improved separator.

  As can be seen from FIGS. 13 and 14, and in particular from FIG. 15, the internal components of the valve unit 14 'are arranged entirely in a housing 12' separated from the rotating body housing 4 '. In more detail, the valve unit housing 12 'conforms to each other to form a sealed and closed space in which the internal components of the valve unit 14' are disposed. Sites 203 and 205 are provided. Referring to FIG. 15, a boss 207 is provided at the upper end of the first portion 203 of the valve unit housing 12 ′, through which a screw thread fixing member 16 ′ is connected to a further boss 209 on the rotating body housing 4 ′. It is extended for screwing.

  Also from FIG. 15, the lower end of the first portion 203 of the valve unit housing 12 ′ extends away from the valve unit housing 12 ′ into the rotating body housing 4 ′ through the outlet hole 10 ′ in the rotating body housing 4 ′. It can be seen that a substantially cylindrical portion 211 is provided. An O-ring sealing member 213 is disposed on the outer surface of the cylindrical portion 211 and faces the interior of the rotor housing 4 'in the assembled separator 2' (defined on said surface). It is in contact with the shoulder. The shoulder thereby prevents undesired movement of the O-ring sealing member 213 along the cylindrical portion 211 by pushing the portion 211 through the outlet hole 10 'during assembly and the O-ring. The sealing member 213 engages with the hole 10 '. More particularly, the O-ring sealing member 213 is sealingly engaged with the internal cylindrical surface of the boss 202 surrounding the outlet hole 10 '.

  An O-ring sealing member 213 is provided toward the proximal end of the cylindrical portion 211 (ie, the end of the cylindrical portion adjacent to the remaining portion of the valve unit housing) to provide a second O-ring sealing member. 215 is provided on the outer surface of the free end (far from the base end) of the cylindrical portion 211. As in the case of the first O-ring sealing member 213, the second O-ring sealing member 215 abuts against the shoulder facing the interior of the rotating housing 4 'so that the sealing member is assembled. As it is pushed into the final use position in the machine 2 ', it prevents unwanted movement of the second O-ring sealing member 215. More particularly, it can be seen from FIG. 15 that in the assembled separator 2 ′, the second O-ring sealing member 215 is sealingly engaged with the outlet 150 of the housing insert 72 ′. The

  A first O-ring sealing member 213 prevents leakage of cleaned gas and / or oil droplets from between the rotor housing 4 'and the valve unit housing 12' and thereby separator 2 '. It will also be appreciated by those skilled in the art to prevent undesirable leakage from the environment to the environment. A second O-ring sealing member 215 prevents oil droplets from leaking into the outlet 150 ′ of the housing insert 72 ′ and thereby cleans out the rotator housing 4 ′ via the cylindrical portion 211. It will be further understood by those skilled in the art that the gas being purified is prevented from being contaminated. The small outer diameter of the cylindrical portion 211 and the first and second O-ring sealing members 213, 215 (as compared to the large diameter O-ring sealing member 160 of the conventional separator 2) is two Allows the use of relatively small manufacturing tolerances that ensure a low failure rate for O-ring sealing members 213, 215. In this regard, for example, it is welcomed that the degree of deflection in the relatively small diameter cylindrical part 211 is less than in the relatively large diameter rotor housing 4 of the conventional separator 2.

  A second boss 207 disposed on one side of the cylindrical portion 211 is provided at the lower end of the first portion 203 of the valve unit housing 12 ′. As in the case of the first boss 207 provided at the upper end of the first portion 203, the second boss 207 at the lower end of the first portion 203 is connected to the second boss 209 provided at the lower end of the rotating body housing 4 ′. The conventional screw screw fixing member 16 'for the screw screw engagement is received (see FIG. 18 for the second bosses 207 and 209).

  The valve unit housing 12 'is a separate housing for the rotating body housing 4', and its structure (except for mating with the cylindrical portion 211 by the outlet hole 10 'and for demarcating the upper and lower pair of bosses 207, 209) As a result of being independent, the rotor housing 4 ′ of the improved separator 2 ′ has an overall shape that is closer to a cylindrical one than the rotor housing 4 of the conventional separator 2. . In this regard, a relatively complex and bulky molded profile that contributes to forming a portion of the conventional valve unit housing 12 (rather than just a mating interface with it). Note that it is equipped on one side. However, referring to FIG. 15, it can be seen that the rotor housing 4 'of the improved separator 2' does not have the complex and bulky forming profile as described above.

  As a result of the rotor housing 4 ′ having a shape close to that of a cylindrical shape, the housing 4 ′ has a reduced amount of deflection during the cooling process compared to the housing 4 of the conventional separator 2. It can be manufactured using injection molding techniques. This allows easier axial alignment of the top and bottom bearing units 50 ', 90'. Furthermore, the rotator housing 4 'shown in the accompanying drawings is similar to the boss 209 of the rotator housing 4' (as in the case of the valve unit housing 12 'shown in FIG. 15). The alternative valve unit may be connected to the valve unit 14 'shown in the accompanying drawings, provided that the alternative valve unit has a cylindrical portion 211 that is suitable for matching. I can do it. For example, if an alternative valve unit has the same cylindrical portion and two bosses as the cylindrical portion 211 and boss 207 shown in FIG. If so, the alternative housing would be significantly larger than the valve unit housing 12 'shown in FIG. 15 and shown in the accompanying drawings. An internal valve structure which is totally different from that of the valve unit 14 'can be stored. This allows the modular structure of the separator 2 'with an increased common area between the different structures of the separator.

  Referring to FIG. 15, the housing 12 'of the valve unit 14' is provided with a raised annular shoulder 18 'defining a fluid outlet through which the gas being cleaned passes from the separator 2'. It can be seen that. The annular shoulder 18 'provided on the valve unit housing 12' is substantially the same as the annular shoulder 6 'provided on the rotating body housing 4'. Thanks to their identity, the inlet and outlet shoulders 6, 18 can interchangeably accept inlet / outlet nipples having the same interface profile. The same inlet / outlet nipple 22 ′ having a 90 ° bend is shown in FIG. The inlet nipple 22 ′ is shown in cross-section, consistent with the shoulder 6 ′ of the rotator housing 4 ′ and further shown in FIG. 17 separated from the shoulder 6 ′.

  As seen most clearly from the side cross-sectional view of FIG. 16, the inner surface 216 of the nipple 22 'has a 90 ° bend and a fluid flow path with a radius on both the outer and inner corners. In combination with the curved surface of the shoulder 6 '. As a result, the tendency of the flow to move away from the inner corner of the bend is greatly reduced compared to the fluid flow on the sharp corner 40 of the conventional configuration. In turn, the pressure loss is also reduced. The interface between the inlet / outlet nipple 22 'and the individual housing shoulders 6', 18 'is now referred to the rotor housing shoulder 6' (which is the same as the shoulder 18 'of the valve unit housing 12'). Will be described in more detail.

  As shown in FIGS. 16 and 17, the rising shoulder 6 'of the rotator housing 4' is centered on a longitudinal centerline that is concentric with the centerline 64 'of the rotator housing 4'. It is provided as an annular boss having a substantially cylindrical wall 217. At the free end of the cylindrical wall 217 (separated from the rest of the rotating housing 4 ') is a curved surface 221 that extends inwardly into the hole formed by the shoulder 6'. A circumferential lip 219 is provided. In cross section (see FIG. 16), the curved surface 221 has a partial circular shape and extends through an arc 223 of approximately 110 °. The partial circular surface 221 is oriented so that the radius 225 of the surface 221 extends parallel to the longitudinal axis of the cylindrical wall 217. In the particular structure shown in FIG. 16, the arc 223 through which the partial circular surface 221 passes terminates at the radius 225 described above. The outer cylindrical surface 227 of the shoulder 6 ′ is concentric with the radial 225 and intersects the partially circular surface 221 to form the upper edge 229 of the shoulder 6 ′.

  Referring again particularly to FIG. 16, the nipple 22 'has a ridge 22' with an inner surface 216 of the nipple 22 'combined with a partial circular surface 221 of the shoulder 6' to cause pressure loss, upstream / downstream. It is understood that a contour is provided to match the shoulder 6 'to provide a smooth surface without facing shoulders, discontinuities, and / or any other features. More specifically, the shape of the nipple 22 'is combined (in any direction through the nipple 22') with the transition from the inner surface 216 of the nipple 22 'to the partial circular surface 221 of the shoulder 6'. It does not appear to provide an obstruction or other pressure drop feature to the fluid flow over the surface. Given the symmetry of the shoulder 6 ', this is a case independent of the angular or polar positioning of the nipple 22' relative to the housing 4 '.

  The smooth transition between the inner surface of the nipple 22 ′ and the partial circular surface 221 causes the internal nipple surface 216 to be at any point where the internal nipple surface 216 meets the partial circular surface 221. This is achieved by the improved separator 2 'structure by shaping the inner surface of the nipple 22' so that it is directed tangential to the partially circular surface 221. Thus, for the inner corner of the bend formed by the nipple / shoulder combination, the inner nipple surface 216 meets the partial circular surface 221 at the aforementioned edge 229 of the shoulder 6 ', and at this point of encounter: It is oriented perpendicular to the aforementioned radial 225 (ie, tangential to the partial circular surface 221). The point where the internal nipple surface 216 meets the partial circular surface 221 of the shoulder 6 'is as it progresses circumferentially around the shoulder 6' to the outer corner of the bend formed by the nipple / shoulder combination. , Sequentially moving radially inward over the partial circular surface 221. The internal nipple surface 216 can be seen in FIG. 16 to coincide with the partial circular surface 221 at the edge 231 of the internal nipple surface 216.

  In practice, the transition between the partially circular surface 221 and the internal nipple surface 216 can result in discontinuities or other pressure losses, due to the limitations and cost constraints of injection molding technology with high tolerances. Naturally there is no freedom from the characteristics of the occurrence. Specifically, a gap is created between the edge 231 of the nipple 22 'and the partial circular surface 221 of the shoulder 6'. In practice, this gap can be reduced by making one or both of the nipple 22 'and the partially circular surface 221 from steel (or other metallic material) by die casting techniques.

  The nipple 22 'is further provided with a generally cylindrical shoulder in the form of a cylindrical wall 233 having an inner diameter and an outer diameter equal to those of the cylindrical wall 217 of the housing shoulder 6'. The cylindrical wall 233 of the nipple 22 'is concentric with the cylindrical wall 217 of the housing shoulder 6' when the nipple 22 'is placed on the shoulder 6'. A curved wall 235 extends radially outward from the aforementioned inner nipple surface edge 231 to the upper edge of the nipple cylindrical wall 233. In cross section, the curved wall 235 is partially circular and is configured to be concentric and abut with the partial circular surface 221 of the housing shoulder 6 '.

  Two fins 237 are disposed on the outer surface of the nipple 22 'and extend from the curved wall 235 to provide additional rigidity to the wall 235 and between the wall 235 and the rest of the nipple 22'. To prevent or reduce the bending of the nipple 22 '(see FIG. 13).

  As in the conventional separator 2, the nipple 22 'of the improved separator 2' is manufactured using conventional injection molding or die casting techniques, resulting in a sharp inner corner 239 (see FIG. See 34). The corner 239 can be considered similar to the inner corner 40 of the conventional nipple 22. However, the presence of the partial circular surface 221 of the housing shoulder 6 'in combination with the improved nipple 22' ensures that a radius is provided to the inward portion of the channel bend in the housing 4 '. I have to. As can be seen from the foregoing, this is independent of the angular orientation of the nipple 22 'relative to the housing 4'. Fluid separation from the inner surface of the bend is thereby reduced or avoided, and pressure loss in this part of the flow path is likewise reduced or avoided.

  Finally, with respect to the shape of the nipple 22 ', the second end of the nipple (away from the end where the housing interface contour is provided) grips a hose located on the nipple second end in use. For this purpose, teeth or serrated projections 38 'are provided on the outer surface.

  Again, it is emphasized that the rotating housing shoulder 6 'is the same as the shoulder 18' on the valve unit housing 12 'and the outlet nipple 22' is the same as described above with respect to the rotating housing shoulder 6 '. It is connected to the second housing shoulder 18 '.

  From the foregoing, it can be seen that the nipple 22 'can be rotated without being disturbed while being placed and abutting on the shoulder 6' as shown in FIG. As such, the nipple 22 'can be spun welded to the shoulder 6' and the nipple 22 'can be secured to the housing in the desired angular orientation. It is welcomed by those skilled in the art that this method of securing the nipple 22 'does not require the use of threaded fasteners as in conventional separators 2. This spin welding technique allows the nipple 22 'to be fixed in any orientation relative to the housing 4' and is circumferential (or closed) without the need for an O-ring seal. It is also understood to provide a ring seal. Specifically, the heat generated by the frictional forces acting between the abutment surfaces of the housing 4 '(ie shoulder 6') and the nipple 22 'during the relative rotation of these surfaces is This results in melting of the surface. The rotation is then stopped and the surfaces solidify, thereby joining together.

  While the rotary welding described above is an effective method of joining to the material of the nipple 22 'to the material of the housing 4', other methods of joining the material can also be used (eg, adhesive bonding, ultrasonic bonding, Or vibration bonding).

  The internal components described above will now be described in more detail with particular reference to FIG.

  First, the top bearing unit 50 ′ is fixed to the inner surface of the rotating body housing 4 ′ immediately after the fluid outlet 8 ′. The top bearing unit 50 'is the same as the top bearing unit 50 of the conventional separator 2, and is a caged bearing that is trapped between an upper steel cap member 54' and a lower bearing seating member 56 'of plastic material. ) 52 '. The top bearing unit 50 ′ (and also the bottom bearing unit 90 ′) is provided with roller bearings (as in the conventional separator 2), but with a slide or friction bearing instead. good.

  More specifically, the bearing seating member 56 'is circular and arranged in the assembled separator 2' in the cylindrical wall 60 'of the rotary housing 4' (without abutting the side) (cap) It has a cylindrical wall 58 'projecting downward (which houses the lower part of the member 54'). The cylindrical wall 60 'extends downward from the upper inner surface of the rotating body housing 4'. A circular ridge 238 also extends downward from the upper inner surface of the rotator housing 4 'and is located radially inward of the first cylindrical wall 60'. The cylindrical wall 60 ′, the circular ridge 238, and the shoulder 6 ′ described above are positioned concentrically with each other and are centered on the center line 64 ′ of the rotator housing 4 ′. It is.

  As will be described in more detail below (with reference to FIGS. 37 to 41), the top bearing unit 50 ′ is secured to the upper inner surface of the rotating body housing 4 ′ by rotational welding techniques. Specifically, the lower bearing seating member 56 ′ is welded to the ridge 238. As in the conventional separator 2 ', no screw fixing member is used to fix the top bearing unit 50' to the rotating body housing 4 '. Such a configuration appears that the center line of rotation of the top bearing unit 50 'is concentric with the center line 64' of the rotor housing 4 '.

  Three partial circular slots 66 '(only two are shown in FIG. 34) are provided in the top bearing unit 50' (indicated by arrows 68 '). Allow flow of inlet fluid therethrough. Upper cap member 54 'diverts the inlet fluid from caged bearing 52'. As in the conventional separator 2, the lower side of the uppermost portion of the cap member 54 ′ (in the caged bearing 52 ′) is also lubricated to move upward through the rotating shaft during use. Divert oil mist.

  The remaining internal components of the separator 2 'are separately assembled with respect to the rotor housing 4' and are therefore partly movably arranged in the housing 4 'as an integral assembly. . As with conventional separators 2, this unitary assembly includes a first group of components that remain stationary with respect to the rotator housing 4 'during use, and the rotator housing 4 during use. '(And the valve unit housing 12') and a second group of components that rotate about a center line 64 'relative to both the first group of components.

  The first group of components comprises an annular bearing plate 70 'and a dish-shaped housing member / insert 72'. As in the conventional separator 2, the housing insert 72 ′ and the bearing plate 70 ′ are cleaned in combination with each other before the separated oil and cleaned gas are discharged from the rotor housing 4 ′. It functions to segregate the oil separated from the gas. The bearing plate 70 'is made of steel and the housing insert 72' is made of a plastic material. The bearing plate 70 ′ and the housing insert 72 ′ are mutually connected by three screw screw fixing members 74 ′ (see FIG. 29) that are screwed with a boss 76 ′ protruding downward from the lower side of the housing insert 72 ′. It is fixed. The bearing plate 70 'closes the open end of the rotor housing 4' and provides an enclosed interior space of the housing 4 'in which some of the second group of components are disposed. In this regard, the rotator housing 4 'defines an internal space for receiving components for separating materials (eg, oil and gas) and directing the separated material from the internal space to different outlets. Can be referred to as the first housing part. The bearing plate 70 ′ can be considered as a second housing part that defines the internal space together with the first housing part.

  This first group of components will be discussed in more detail later in this description.

  The second group of components forms a rotating assembly and a plurality of individual separating disks 82 which together form a stack 84 'of rotating shaft 78', upper rotating disk 80 'and separating disk 82'. ', Fan disk 240, end member / plate 86', splash guard disk 242, and combined fan and turbine unit 88 '. The rotating shaft 78 'is made of a metal material, and the remaining components of the second group described above are made of a plastic material by an injection molding technique. The second group of previously described components are secured to one another to prevent or at least limit their rotation relative to one another. A helical compression spring (of metallic material) is also provided in the second group of components, as will be described in more detail below. The second group of components is rotatably provided by the bottom bearing unit 90 'relative to the first group of components, and in the assembled separator 2', rotated by the top bearing unit 50 '. It is provided so as to be rotatable with respect to the body housing 4 '.

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

  The axis of rotation 87 has an annular cross section to provide a fluid flow path 92 'that extends longitudinally along its entire length. During use of the separator 2 ', the flow path 92' lubricates the bearings of the unit 50 'by the oil mist moving upwards from the turbine vessel into the top bearing unit 50' via the rotating shaft. Is acceptable. A number of recesses and shoulders are provided outside the rotating shaft 78 'to help the remaining components be in the correct axial position on the rotating shaft 78'.

  Each of the upper rotating disc 80 ', the separating disc 82', the fan disc 240, and the end plate 86 'is connected in use to a central hub element disposed about the rotating shaft 78'. A truncated frustoconical portion (which defines upper and lower truncated frustoconical surfaces).

  In the case of the upper rotating disc 80 ', the separating disc 82', and the end plate 86 ', it is connected to the corresponding central hub element by a plurality of spoke members extending radially inward therefrom. Yes. These spoke members have an open space between them to allow fluid flow therethrough axially along the axis of rotation 78 '.

  In the case of a fan disc 240, the truncated frustoconical portion 290 is connected to a corresponding central hub element 292 by a second truncated frustoconical portion 294. This second truncated frustoconical portion 294 provides an impediment to flow so that it passes up or down the fan disk 240 along the axis of rotation 78 ′. It is continuous to prevent axial flow of any fluid passing through it.

  The truncated frustoconical shape of the second truncated frustoconical portion 294 has a larger included angle than that of the other truncated frustoconical portions of the improved separator 2 '. In other words, the opposite side of the second truncated frustoconical portion 294 is the first truncated frustoconical portion 290 of the fan disk 240, all having the same included angle. More rapidly than in the case of the upper rotating disc 80 ′, the separating disc 82 ′, and the end plate 86 ′ (and in fact, the frustoconical isolated roof member 268 of the housing insert 72 ′). Diversify / concentrate. The central hub element 292 is a cylindrical wall that rises from the second frustoconical portion 294 (see in particular FIGS. 26 and 33). A longitudinally extending slot 296 (only one of which is shown in FIG. 26) receives a fan to receive a spline 254 extending radially from the rotation axis 78 '. The hub element 292 is provided through the entire thickness of the cylindrical wall. In this way, the rotation of the fan disk 240 with respect to the rotating shaft 78 'is prevented.

  Below the first truncated frustoconical portion 290 of the fan disk 240, there are a plurality of caulk members 298 spaced equally around the center line of the fan disk 240. Is provided. Each caulk member 298 is provided as a linear ridge projecting downwardly from the underside of the first truncated frustoconical portion 290 and the radius of the first truncated frustoconical portion 290 is provided. Extending radially from the inner edge in the direction to the radially outer edge of the first truncated frustoconical portion 290. In the assembled separator 2, the caulk member 298 abuts the upper surface of the truncated frustoconical portion of the end plate 86 'and thereby passes through it (in FIG. 34). It ensures a space between the fan disk 240 and the end plate 86 'through which fluid can flow (as indicated by arrow 188'). During use of the separator 2 ', rotation of the caulk member 298 imparts rotational motion on the fluid between the fan disc 240 and the end plate 86'. As a result, the fluid is moved outward to the cylindrical wall 201 of the rotator housing 4 '. Oil droplets (and / or in fact liquid or particulate contaminants carried by the gas stream) are effectively thrown against the cylindrical wall 201 of the rotor housing 4 'and the bearing plate It flows downward (or falls) onto 70 '. Gaseous fluid discharged from the space between the fan disc 240 and the end plate 86 'may also flow downward onto the bearing plate 70' or as described in more detail below. Either exit the housing 4 'directly.

  With respect to the end plate 86 ', the radially inner circular edge of the truncated frustoconical portion 108' is connected to the central hub element 98 'by a plurality of spoke members 110' (see FIG. 18). However, the cylindrical wall 300 also extends downward from the radially inner edge of the frustoconical portion 108 '. In the assembled separator 2 ′, the cylindrical wall 300 is centered on the center line 64 ′ and extends through a central hole provided in the insert housing 72 ′ so as to extend through a rotation shaft 78. It extends sufficiently downward along ´. Although the wall 300 has a substantially cylindrical shape, the inner surface 302 of the wall 300 is reduced in the upward direction in the separator 2 ′ in which the inner diameter of the cylindrical wall 300 is assembled. A truncated frustoconical shape is defined. The outer cylindrical surface of the wall 300 has substantially the same diameter as the central hole of the housing insert 72 ', and in the assembled separator 2', the wall 300 and the insert housing 72 ' Located in the hole with minimal space in between. This close fit allows relative rotation between the end plate 86 'and the insert housing 72' while flowing between the wall 300 and the central hole of the insert housing 72 '. Helps reduce the amount of separated oil that contaminates the gas being cleaned. Furthermore, the internal truncated frustoconical surface 302 of the wall 300 functions to limit the passage of oil droplets flowing upward into the space between the fan disc 240 and the end plate 86 '. To do. It is well known in the art that oil drops in contact with the frusto-conical surface of the wall 300 are subject to rotational motion and forces acting downward due to the frusto-conical shape of the surface. To be understood by those who are.

  The splash guard disc 242 is arranged above the rotary shaft 78 'in the assembled separator 2' by six spoke members 306 extending radially inward therefrom. A flat annular disc 304 connected to a central hub element 308 that is connected. The diameter of the central hole defined 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 flow of fluid passing through the splash guard disc 242 and into the region between the fan disc 240 and the end plate 86 ′ is therefore the splash guard disc 242. It does not encounter a feature that causes significant pressure loss at the junction with end plate 86 '. The annular disk 304 provides a flange member extending radially from the lower end of the cylindrical wall 300 and, in use, the outer surface of the cylindrical wall 300 and the cylindrical wall through the outer surface. 300 functions to cover any space between the portion of the housing insert 72 'defining the central hole through which it extends. In this way, the flat annular disk 304 is cleaned by splashing separated oil droplets or otherwise moving upward from the bearing plate 70 'through the central hole of the insert housing 72'. Reduce the tendency to contaminate gas.

  The region between the fan disc 240 and the end plate 86 ′ is such that the fluid inlet port 618 (defined by the splash guard disc 242), as shown in FIG. It is further welcome to define a flow path 616 that passes from the outlet 620 (defined by the radially outer periphery of the fan disk 240 and end plate 86 ').

  The hub element 308 of the splash guard disc 242 is provided as a cylinder, the upper end of which is relative to the longitudinal centerline of the cylinder (and in the assembled separator 2 ', the centerline 64). It is closed by a flat wall arranged at a right angle (to '). The inner diameter of the cylinder is larger than the outer diameter of the rotating shaft 78 ', and the flat wall is provided with a central hole through which the shaft 78' passes in the assembled separator 2 '. It has been. In the assembled separator 2 ′, this configuration pushes the splash guard disc 242 against the end plate 86 ′ against the rotating shaft 78 ′ and the cylinder of the hub element 308, and thus a fan (fan). ) Define an annular space between them to receive the helical compression spring 96 ′ that pushes against the disc 240 and the disc stack 84 ′ upward rotating disc 80 ′.

  The splash guard disc 242 is manufactured separately from the end plate 86 'to allow the cylindrical wall 300 of the end plate 86' to be placed through a central hole, such as the insert housing 72 '. Has been. This is because the outer diameter of the annular disc 304 is larger than the diameter of the central hole in the housing insert 72 ', so if the splash guard disc 242 is integral with the end plate 86'. Is possible.

  As is apparent from the foregoing, the truncated frustoconical shape of the upper rotating disc 80 ', the fan disc 240 (with respect to its first truncated frustoconical portion), and the end plate 86' It is substantially the same as that of the plate 82 '. This allows the upper rotating disc 80 ', the fan disc 240, and the end plate 86' to be stacked with the separating disc 82 ', where the upper rotating disc 80' is separated. Arranged at the top of the disk stack 84 ′ and an end plate 86 ′ is disposed at the bottom of the separated disk stack 84 ′. A fan disk 240 is disposed between the end plate 86 'and the lowermost (ie, bottom) separation disk 82' in the separation disk stack 84 '.

  Furthermore, the separation disk 82 'is relatively thin to allow a large number of disks to be provided in the relatively short stack 84', and the upper rotating disk 80 'and end plate 86' are separated by the separation disk 82 '. Which is much thicker than that and provides rigidity to either end of the disc stack 84 'so that the compression axial force is exerted by the upper disc 80' and the end plate 86 'on the truncated frustoconical part of the separating disc 82'. It will be understood by those skilled in the art that the present invention applies equally. The compressive force is generated by the helical compression spring 96 ′ that pushes the lower side of the hub 308 of the splash guard disc 242 upward. Next, the hub 308 of the splash guard disc 242 pushes the lower side of the abutment hub 98 'of the end plate 86' upward.

  Regarding compression of the disk stack 84 ′ between the upper disk 80 ′ and the end plate 86 ′, the adjacent separating disk 82 ′ in the stack 84 ′ is improved as in the conventional separator 2. Those skilled in the art will appreciate that they must remain separated from one another in order to allow fluid flow through the separated separator 2 '. This space of the separation disk 82 ′ is provided by a plurality of spacers 246 in the improved separator 2 ′. The individual spacers 246 are small protrusions that are positioned and raised on the upper surface 102 'of the truncated frustoconical portion 124' of the individual separator disk 82 '(see FIG. 20).

  The lowest separating disc 82 'in the stack 84' can also optionally be spaced away from the fan disc 240 to allow fluid flow therebetween. If such a space is required, then appropriate spacers are used. Ideally (located below the frustoconical portion of the disk stack 84 'and connected to the fan disc hub by the second frustoconical portion of the fan disc 240 A spacer 246 is provided on the upper surface of the first truncated frustoconical portion of the fan disk 240 in the same manner as the truncated frustoconical portion of each individual disc 82 '. .

  Each of the spacers 246 has a circular shape, but other shapes can be used (eg, an oval shape can be used). Any alternative shape for spacer 246 preferably has a curved edge to reduce fluid pressure loss in the fluid flowing through the spacer.

  A first group of spacers 246 is arranged in a concentric circle adjacent to the inner circular edge 104 ′ of the upper surface 102 ′. The individual spacers 246 in this first group are located adjacent to the portion of the inwardly circular edge 104 'where the spokes of the disc 82' are joined to the frustoconical portion of the disc 82 '. Yes. A second group of spacers 246 is arranged in a concentric circle adjacent to the outer circular edge 106 'of the upper surface 102'. A third group of spacers 246 is arranged in a concentric circle approximately midway between the inner and outer circular edges 104 ′, 106 ′ of the truncated frustoconical part of the disc 82 ′.

  As will be described in more detail below, individual separation discs 82 '(and, in fact, fan discs 240) rotate at one of only three possible angular positions relative to axis of rotation 78'. The positioning of the spacer 246 on the shaft 78 'and the positioning of the spacer 246 on the upper surface 102' is the spacer of the adjacent disc 82 'when the disc 82' is placed in any of these three positions. It appears that 246 must be aligned with each other. In other words, when the separation discs 82 'are pushed axially on the rotation shaft 78' and abut against each other to form the aforementioned laminate 84 ', (i) each of the particular discs 82' Spacers 246 are located immediately above spacers 246 of adjacent discs 82 'disposed under said particular discs 82' in the stack 84 ', and (ii) each of the particular discs 82' Naturally, the spacers 246 are located directly below the spacers 246 of the adjacent discs 82 ′ disposed on the specific discs 82 ′ in the stack 84 ′. As a result, the compressive force applied to the disk stack 84 ′ by the end plate 86 ′ is transmitted through the stack 84 ′ by the aligned spacers 246 without closing the space between adjacent separating disks 82. . This ensures that fluid can be maintained between the separation discs 82 '.

  It can be seen from the drawings that the spacers 246 preferably have a small radial dimension as well as a small circumferential dimension relative to the dimension (diameter) of the corresponding separating disk. This allows fluid to flow relatively undisturbed by the spacers in the circumferential direction across the disk upper surface 102 'and also in the radial direction across the surface 102'. This ensures that the pressure loss in the fluid flow between adjacent discs 82 'is minimized.

  The upper rotating disc 80 'and the rotating shaft 78' are shown apart from the other components of the separator 2 'in FIGS. 21 and 23 of the accompanying drawings. A hub 114 ′ of the upper rotating disk 80 ′ is provided on the outer surface of the rotating shaft 78 ′ and thereby joined to the shaft 78 ′. This joint prevents relative rotation between the hub 114 'and the rotating shaft 78'.

  The hub 114 'of the upper rotating disc 80' extends axially upward along the rotational axis 78 'and ends at the upper end of the shaft 78'. The upper part of the rotary shaft 78 ′, around which the second helical compression spring 130 ′ is located, is therefore provided with a coating (sleeve) of plastic material (preferably thermoplastic material). This coating protects the spring 130 ', and in particular the shaft 78', from fretting corrosion. A first and second group of internal components of an alternative embodiment relative to the first embodiment 2 'are shown in FIG. The alternative separator is the same as in the first embodiment, except that the upper end portion of the rotating shaft 78 'has no plastic coating adjacent to the second helical spring 130'.

  The hub 114 'of the upper rotating disc 80' also extends axially downward along the rotating shaft 78 'and ends at a point directly above the bottom bearing unit 90'. The bottom bearing unit 90 'therefore contacts the metal end of the rotary shaft 78' in the assembled separator 2 '. More particularly, the hub 114 ′ extends along the entire depth of the separation disk stack 84 ′ and therefore separates the hub 120 ′ of the individual separation disk 82 ′ from the rotational axis 78 ′. It is also understood that the hub 114 ′ also provides a coating (sleeve) of plastic material (preferably thermoplastic material) on the rotating shaft 78 ′ in the region of the first helical compression spring 96 ′. This coating also protects the spring 96 'and in particular the shaft 78' from fretting corrosion.

  The truncated frustoconical portion 112 'of the upper rotating disk 80' is connected to the hub 114 'by twelve radially extending spoke members 116'. Each spoke member 116 ′ has a long rectangular cross section, and its upper (short) side 310 is adjacent to the innermost circular edge 312 in the radial direction of the truncated truncated cone part 112 ′. . Each spoke member 116 ′ extends axially downward from the edge 312. This configuration allows the individual spoke members 116 'to function as fan blades and impart motion on the adjacent fluid when the upper rotating plate 80' rotates during use of the separator 2 '. . As will be appreciated by those skilled in the art, the movement imparted on the fluid by the individual spoke members 116 ′ causes the fluid to flow tangentially from the circular passages of the spoke members 116 ′ and the truncated cones. As a result, it is effectively thrown outward toward the cylindrical wall of the rotating body housing 4 ′ through the disk stack 84 ′ in the vicinity of the base portion 112 ′. The function of the spoke member 116 ', such as a fan blade, is that the rotation of the upper rotating disc 80' (as indicated by arrow 68 'in FIG. 34) is through the fluid inlet 8' and between the spoke members 116 '. Result in drawing gas into the rotator housing 4 'through the space 600, whereby the space 600 provides an inlet to the rotator assembly.

  Fluid entering the rotor housing 4 'passes through the three partial circular slots 66' in the top bearing unit 50 '. The spoke member 116 ′ of the upper rotating disk 80 ′ is arranged directly below the three partial circular elongated holes 66 ′ in the assembled separator 2 ′. Referring specifically to FIG. 34 of the accompanying drawings, the radial dimension of the partially circular slot 66 'is shorter than the radial dimension (ie, length) of the spoke member 116', and a large amount of incoming fluid. It can be seen that the portion collides minimally only with the length of the spoke member 116 'which is arranged directly adjacent to the partial circular slot 66'. This length of the individual spoke element 116 ′ is provided with a curved fluid guide vane 314 extending upward from its upper side (or leading edge) 310. The purpose of the individual guide vanes 314 is to reduce or eliminate the pressure loss corresponding to the separation of the inlet fluid from the spoke members 116 '. This appears to have an aerodynamically shaped cross-section and a substantially zero angle of attack (or other angle of attack that does not result in fluid separation from the guide vanes 314) with the incoming flow of fluid. This is achieved by providing a substantial axial flow of the inlet fluid into the rotor housing 4 'by means of a guide vane having a directed chord.

  A cross-sectional view through the length of the spoke member 116 'provided with the guide vanes 314 is shown in FIG. The surface of the guide vane 314 functions to guide fluid approaching the leading edge 310 of the spoke member 116 'to align with the spoke member 116'. A chord 316 corresponding to the leading edge 318 of the guide vane 314 is oriented to have a substantially zero angle of attack with the fluid flowing over the guide vane 314. The direction of this fluid relative to the guide vanes 314 is indicated by arrow 320 and, as indicated in FIG. 22, (i) inlet fluid flow (Q / A, where Q is the volume through the inlet. And (ii) the tangential velocity of the guide vane 314 (ω.r, where ω is upwardly rotated), and A is the cross-sectional area of the inlet channel It is understood that this is a function of the angular velocity of the disc, and r is the radial distance of the guide vane from the center of rotation. Since the direction of fluid flow 320 with respect to the guide vane 314 depends on the radial position along the guide vane 314, the chord 316 can be oriented at an angle that varies at the radial position. In other words, the fluid guide vane 314 can be twisted to ensure that the guide vane 314 is properly aligned with the incoming fluid flow at all radial positions along the guide vane 314. . More specifically, the acute angle 322 between the chord 316 and the vertical reference line 324 (which is parallel to the center line 64 'in the assembled separator 2') is the innermost along the spoke member 116 '. Can be increased sequentially from one radial position to the outermost radial position.

  During use of the improved separator 2 ', incoming air flows axially downwards through three partial circular slots 66' and below the slots 66 '. It collides with the guide vane 314 arranged at a short distance and rotates in a circular passage around the center line 64 '. Since the chord 316 of the leading edge 318 of each guide vane 314 is oriented to have a substantially zero angle of attack with respect to the incoming flow of fluid, the low pressure side 324 and high pressure side 326 of the guide vane 314 The fluid flows over both and is guided to flow axially relative to the spoke member 116 ′ without detachment from the guide vane 314 or the corresponding spoke member 116 ′. The pressure loss caused by the fluid flowing through the upper rotating disk 80 'is thus avoided or minimized.

  A further consequence of the reduced pressure drop provided by the guide vanes 314 is that the spokes (as compared to the conventional separator 2) without an overall undesirable effect on the fluid flow rate through the separator 2 '. The number of members 116 'can be increased. The increased number of spoke members 116 'allows a greater compressive force to be transmitted between the truncated frustoconical portion 112' of the upper rotating disc 80 'and the hub 114'. An increased number of spoke members 116 'can also improve the balance of the upper rotating disc 80'.

  FIG. 22 provides a schematic view of guide vanes 314 and corresponding spoke members 116 ′ and is not necessarily a representative of a particularly preferred shape or actual particularly preferred rotational speed and fluid flow rate.

  Referring to FIG. 21, a cylindrical rim 328 is seen that is concentric with and rises from the radially innermost edge 312 of the truncated frustoconical portion 112 '. In the assembled separator 2 ', the rim 328 is arranged radially outwardly from a cylindrical wall 58' projecting below the top bearing unit 50 '. The rim 328 is nevertheless placed close to the cylindrical wall 58 'to prevent (or very restrict) fluid leakage between them (see especially FIG. 34). As can be seen most easily from FIG. 23 of the accompanying drawings, three splines 254 extend radially from the hub 114 ′ of the upper rotating disc 80 ′. The three splines 254 are equally spaced around the longitudinal centerline of the upper rotating disc 80 'and, from the lower side 330 of the spoke member 116', in the assembled separator 2 ', a fan ( fan) extends axially along hub 114 '(and consequently along axis of rotation 78') to a point along hub 114 'located approximately midway along central hub element 292 of disc 240. I'm out.

  Each spline 254 has a base portion 350 and a top portion 352. The base portion 350 is joined to the remaining portion of the hub 114 '. Top portion 352 is adjacent to base portion 350 and provides a free end to spline 254. The base portion 350 of each spline 254 is wider (ie, has a greater circumferential dimension) than the top portion 352. As a result of the different widths of the base and top portions 350, 352, a step 354 is provided on either side of the individual spline 254 at the intersection between the base and top portions 350, 352. With particular reference to FIG. 23, it can be seen that the width of the base portion 350 of the individual spline 254 increases from the lower end of the individual spline 254 to the upper end of the individual spline 254. Further, the width of each foundation portion 350 is approximately equal to the width (ie, circumferential dimension) of one of the twelve spokes 116 'of the upper rotating disc 80'. The top portion 352 of each spline 254 is also circumferentially aligned with and adjacent to the spoke member 116 '.

  The hub 120 'of the individual separating disk 82' has a hole 252 through which the rotating shaft 78 'and the upper rotating disk hub 114' extend (see especially FIGS. 23, 24 and 25). . The rotational movement of the separating disc hub 120 'relative to the upper rotating disc hub 114' (and thus relative to the rotating shaft 78 ') is provided axially along the length of the upper rotating disc hub 114'. Blocked by three splines 254 extending radially into the corresponding female mating contour defined by the holes 252 in the disc hub 120 '. This arrangement of the splines 254 prevents lateral and rotational movement of the separating disc hub 120 'relative to the rotational shaft 78'. More particularly, the surface 356 (substantially radially extending) of the top portion 352 of each spline 254 is relative to the separation disk 82 'and the upper rotating disk hub 114' (and the rotating shaft 78 '). Abuts the corresponding surface 358 of the mating contour (also extending substantially radially) to prevent general rotation. The abutting surfaces 356, 358 are welcomed to abut each other in use in a direction substantially orthogonal to each of the surfaces 356, 358, and for this reason, each of the surfaces 356, 358 Said relative sliding is negligible or not at all and can lead to increased or undesired relative rotation between the separating disc 82 'and the upper rotating disc hub 114'. There is little or no corresponding frictional wear of the surfaces 356,358.

  The separation disk hub 120 ′ of each separation disk 82 ′ is connected to the truncated frustoconical portion 124 ′ of each separation disk 82 ′ by twelve radially extending spoke members 126 ′. Yes. As in the conventional separator 2 ', the spokes 126' (and the remaining portions of the corresponding separating disk 82 ') are made of a relatively thin and elastically flexible plastic material. Also, as in the prior art separator 2 ', the spokes 126' can resist the lateral and rotational forces loaded on them without deformation and the compressive force generated by the helical spring 96 '. Are transmitted through the separation disk stack 84 ′ via the spacers 246 rather than by the separation disk spokes 126.

  The relative shape of the spline 252 and the holes 252 of the individual separating disks 82 'is such that the individual separating disks 82' are arranged in one of only three angular positions on the rotation axis 78 'as described above. Make sure you can. Thanks to the positioning of the spacers 246 relative to the holes 252, the polar or angular positioning of the spacers 246 on the separating disk 82 'is in spite of the use of three angular positions relative to the rotation axis 78'. Instead, it remains the same, and therefore there is no possibility of the separation disk stack 84 'being combined on the rotating shaft 78' without the spacers 246 of adjacent separation disks 82 'being aligned. Nevertheless, each individual disc 82 'is provided with a marker that can be aligned with the markers of other discs 82' in the disc stack 84 '. In this case, all the disks 82 'in the stack 84' have the same angular position with respect to the rotation axis 78 '. The marker is provided as a rib 256 that is disposed on the hub between the two spokes 126 'and extends a short distance radially outward.

  For purposes of clarity, Figures 13, 15, 19, 20, 27, 33, 34 of the accompanying drawings show a disk stack 84 'providing a reduced number of separating disks.

  An annular recess 258 (see FIG. 21) concentric with the rotating shaft 78 'is provided in the upper surface of the upper rotating disc hub 211'. Annular recess 258 receives a second helical compression spring 130 'and prevents downward axial movement of this spring 130' along rotation axis 78 '. Furthermore, in the assembled separator 2 ′ (with the upper end of the rotary shaft 78 ′ being away from the cap member 54 ′ of the top bearing unit 50′—see in particular FIG. 34) bearing) 52 'cage abuts the second spring 130' and pushes downward.

  During the assembly of the improved separator 2 ', most of the combined fan and turbine unit 88' of the second group of internal components are interconnected with each other. The upper rotating hub 114 '(and the remaining portion of the upper rotating disc 80') is injection molded with the rotating shaft 78 'in-situ. The stack 84 ′ of separation disks 82 ′ is then slid axially from the lower end along the rotating shaft 78 ′ and comes into contact with the lower side of the truncated cone portion 112 ′ of the upper rotating disk 80 ′. Be placed.

  Before the fan / turbine unit 88 is provided at the lower end of the rotary shaft 78, the lower end of the shaft 78 is a central circular hole provided in the bearing plate 70 and the housing insert 72 of the first group of internal components. Placed through. By doing so, the lower end of the rotating shaft 78 is also extended through the bottom bearing unit 90 which is fixed in the central hole of the bearing plate 70 (see in particular FIGS. 8 and 10).

  With further reference to the compressive force applied to the separating disk stack 84 ', it will be understood by those skilled in the art that this force is generated by the helical compression spring 96'. During use of the separator 2 ′, the compression spring 96 ′ rotates with the rotary shaft 78 ′, and the lower end of the compression spring 96 ′ is in contact with the radial inner race of the bottom bearing unit 90 ′. Push it down and transfer the force upward to the splash guard hub 308. The compressive force is then transmitted from the splash guard hub 308 to the endplate hub 98 '. The rotation of the splash guard 242 relative to the end plate 86 'is resisted by the frictional force between the splash guard hub 308 and the end plate hub 98' (understood as a function of compressive force). .

  Thanks to the rigidity of the end plate 86 ', compressive force is transmitted from the hub 98' to the truncated frustoconical portion 108 'of the end plate 86' via the plurality of radially extending spoke members 110 '. The compressive force is then transmitted to the caulk member 298 of the fan disc 240 via the truncated frustoconical portion 108 ′ and then the truncated frustoconical portion of the fan disc 240. 290 is transmitted upwardly (via spacer 246) through stack 84 'to truncated frustoconical portion 112' of upper rotating disc 80 '. The compressive force is transmitted from the truncated frustoconical portion 112 'to the hub 114' of the upper rotating disc 80 'via twelve radially extending spokes 116'. The compressive force is transmitted from the truncated truncated cone part 112 'to the hub hub 114' due to the rigidity of the upper rotating disk 80 '. The upward axial movement of the upper rotary disc 80 'along the rotary shaft 78' as a reaction to the compressive force causes the upper rotary disc hub 114 'to abut the downwardly facing shoulder 250 on the rotary shaft 78'. Is blocked by the position of. Downward axial movement of the upper rotating disc 80 ′ along the rotating shaft 78 ′ is prevented by the position of the upper rotating disc hub 114 ′ that contacts the upwardly facing shoulder 248 on the rotating shaft 78 ′. Yes.

  Adjacent discs 82 'of the disc stack 84' can optionally be secured together. This increases the rigidity of the disk stack 84 'and increases the rigidity of the adjacent disk 84' and ensures the relative rotational position of the adjacent disks 84 '(ie, disk spacers). 246 remains aligned and ensures that the space between adjacent discs 82 'transmits the compression force without closing). The discs 82 'can be fixed to each other by welding (for example, ultrasonic welding).

  Before the fan / turbine unit 88 'is provided at the lower end of the rotary shaft 78', as in the conventional separator 2 ', the lower end of the rotary shaft 78' is connected to the first group of bearing plates 70 'and the internal components. It is arranged through a central circular hole provided in each of the housing inserts 72 '. The lower end of the rotary shaft 78 'is also extended through a bottom bearing unit 90' fixed in the central hole of the bearing plate 70 '(see especially FIGS. 29 and 30).

  The combined fan and turbine unit 88 ′ is fixed to the lower end of the rotating shaft 78 ′ protruding downward from the lower side of the bearing plate 70 ′. The fan / turbine unit 88 ′ is disposed around the lower end of the circlip 132 ′ and the rotating shaft 78 ′ (held in a circumferential recess in the lower end of the rotating shaft 78 ′). It is held in position on the lower end of the rotary shaft 78 ′ by a helical compression spring 360 abutting the upper facing surface of a circlip 132 ′.

  A circlip 132 'and compression spring 360 are disposed within the cavity of the combined fan and turbine unit 88'. The compression spring 360 pushes upward in the cavity, thereby urging the fan / turbine unit 88 upward and in contact with the radially inner race of the bottom bearing unit 90 '. This configuration is most clearly apparent from FIG. 30 of the accompanying drawings. Referring to this drawing, an upward facing deflector surface 139 'is provided on the unit 88' and is located radially inward of the fan blades 140 'of the unit 88'. Has been. The deflecting surface 139 'performs the same function as the deflector washer 139 in the conventional separator 2, but is provided integrally with the fan / turbine unit 88' rather than the separating abutment component. The radially inward portion of the deflector surface 139 'is pushed upward to abut the inner bearing race of the bottom bearing unit 90' and thus pushed upward against the bearing plate 70 '. The deflector surface 139 'and the radially outer bearing race of the bottom bearing unit 90' are axially separated from each other so that they pass down the bottom bearing unit 90 'and into the turbine vessel. And allowing the separated oil to flow radially outward through the axial space.

  The rotating assembly of separator 2 is rotated in the direction indicated by arrow 134 '(see FIGS. 29 and 30) by a hydraulic impulse turbine. As in the conventional separator 2 ', the fan / turbine unit 88' has a Pelton wheel 136 'having a plurality of buckets 138' spaced equally along its periphery. It has. When the separator 2 'is in use, oil injection is directed from the nozzle (not shown) in the turbine vessel toward the periphery of the Pelton wheel 136'. More particularly, the jet is directed along a tangent to a circle passing through a plurality of buckets 138 'so that the jet enters a bucket that is aligned with its surface. The jet flows along the surface following the internal contour of the bucket and is then reversed by the contour to flow along a further surface and then discharged from the bucket. As a result, the injection rotates the wheel 136 '.

  A fan having a plurality of blades 140 'is also formed integrally with the wheel 136'. The wing 140 'is disposed on the wheel 136' in close proximity to the underside of the bearing plate 70 '. The plurality of vanes 140 ′ are also at substantially the same axial position as the deflector surface 139 ′ and bottom bearing unit 90 ′ along the rotational axis 78 ′. The fan blade 140 ′ extends radially outward from near the bottom bearing unit 90 ′. It will be appreciated by those skilled in the art that the fan blades 140 'rotate about the centerline 64' when the turbine wheel 136 'rotates. By so moving, the fan blades 140 'efficiently throw fluid from the area between the wheel 136' and the underside of the bearing plate 70 ', thereby causing fluid pressure in the area of the bottom bearing 90'. And from the position above the bearing plate 70 ′, helps to draw the separated oil down through the bottom bearing unit and into the turbine vessel 178 below the bearing plate 70 ′.

  For ease of manufacture, the wheel 136 ′ is formed as upper and lower portions 142 ′, 144 ′ and two screw threaded fastening members (only one of which is shown in FIG. 30 of the accompanying drawings). Are pressed against each other at a line 146 '.

  A plurality of fan blades 140 'and deflector surface 139' are integrally formed with the upper portion 142 'of the fan / turbine unit 88'. In the lower part 144 ′ of the fan / turbine unit 88 ′, in the assembled separator 2 ′, the lower part is orthogonal to the center line 64 ′ and opens to the flow path 92 ′ of the rotating shaft 78 ′. A lower plate member 364 is provided lying in a plane across the hole. The plate member 364 is nevertheless spaced from the opening to the flow path 92 'to allow fluid flow into the opening.

  The plate member 364 is provided with four holes 366 arranged at equal intervals along an imaginary circle centered on the center line 64 ′ in the assembled separator 2 ′. Although the holes should be arranged to ensure rotational balance of the fan / turbine unit 88 ', those skilled in the art will appreciate that an alternative number of holes 366 may be used.

  Importantly, the hole 366 is located radially outward from the opening to the channel 92 ′. Thus, the configuration allows oil mist mist to flow upwardly from the turbine vessel through hole 366 and thereby enter the cavity in fan / turbine unit 88 'and flow path 92 of rotating shaft 98'. It will be understood that it seems to flow upward through '. However, it is also welcomed that the flow from the hole 366 to the opening of the channel 92 is directed radially inward. During use of the separator 2 ', the fan / turbine unit 88' is of course rotating in the direction indicated by arrow 134 'and the mist of oil droplets is radially inward from the hole 366 into the flow path 92'. A relatively large amount of the oil body flowing through the holes 366 is moved laterally by the rotating plate member 364 and thrown away from the opening to the flow path 92 ′. For example, in the case of vehicle leaning or other movement, such as oil splashing upwards from the engine casing through holes 366 to flow through the fan / turbine 88 'cavity, the oil in the cavity The lateral movement loaded on the oil prevents the oil from flowing inward toward the rotating shaft 78 '. A large amount of undesired flow of oil upward through the rotating shaft 78 'and into the disk stack 84' is thus avoided.

  Two exhaust holes 368 are provided in the plate member 364 to allow oil to be exhausted from the cavities in the fan / turbine unit 88 'and back to the turbine vessel. The discharge holes 368 are arranged diametrically opposite each other, and form elongated holes in the plate member 364 and in a substantially cylindrical wall rising from the circular periphery of the plate member 364. The position of the discharge hole 368 in the outermost part in the radial direction of the turbine cavity is such that the oil thrown away from the rotating shaft 78 'to the outer periphery of the cavity is efficiently discharged from the fan / turbine unit 88'. Make sure you do.

  The plate member 364 is shown to be integral with the lower portion 144 'of the fan / turbine unit 88' in the embodiment of FIGS. 29 and 30, but is shown in FIGS. 31 and 32 of the accompanying drawings. In an alternative embodiment, the end plate 364 is provided as a circular disc separate from the lower portion 144 of the fan / turbine unit 88 '. Referring to FIGS. 31 and 32, it can be seen that another plate member 364 of the alternative embodiment is a circular disc provided with holes 366 as in FIGS. However, the alternative plate member 364 is secured in place with respect to the rest of the fan / turbine unit 88 ′ by a screw threaded fastening member 362 (extending therethrough) and there is no exhaust hole 368. . In this alternative embodiment, the discharge hole 368 is disposed solely in the cylindrical wall of the lower portion 144 ′ that is concentrically arranged with the circular periphery of the plate member 364 and extends upward therefrom. Is provided. The lower portion 144 ′ of the fan / turbine unit 88 ′ is further disposed in the cavity of the fan / turbine unit 88 ′, and faces downwardly so that the plate member 364 is pressed against the two screw screw fixing members 362. A second cylindrical wall 370 is provided that extends downward to provide an annular surface. A recess is provided in the annular surface that faces downward to provide a fluid passage 372 between the cylindrical wall 370 and the plate member 364. In use, oil flowing outward across the upper surface of the plate member 364 passes through the flow path 372 to the discharge hole 368.

  The fan / turbine unit 88 'of FIGS. 31 and 32 is provided with an outer cylindrical wall and plate member 364, both defining a cavity, and further with a plate member 364 disposed thereon. A further cylindrical wall 370 is provided, and the fan / turbine unit 88 ′ is otherwise similar to that of the conventional separator 2, and the rotational shaft 78 ′ as in the conventional separator 2. It is fixed to. Specifically, the fan / turbine unit 88 ′ pushes upward on the lower portion 144 ′ of the unit 88 ′ and is disposed in a circumferential recess on the outer surface of the rotating shaft 78 ′ ( circlip) 132 and is fixed to the rotating shaft 78 ′ by a washer 133 ′ held at a predetermined position. Washer 133 'and snap ring 132 provide an alternative securing means for compression spring 360 and snap ring 132 shown in FIGS.

  For the first group of internal components, the bearing plate 70 'has a circular shape with a diameter substantially equal to the diameter of the rotating body housing 4'. As in the conventional separator 2 ', the relative shape seems to allow the bearing plate 70' to be placed on the shoulder 148 'facing downward at the lower end of the rotor housing 4'. is there. In this case, the lower opening end of the rotating body housing 4 ′ is closed by the bearing plate 70 ′. However, in the improved separator 2 ′, the lower open end of the rotator housing 4 ′ abuts the upper side of the bearing plate 70 ′ and there is a circumferential recess 260 for receiving the O-ring sealing member 262. Provided (see FIG. 34). It will be appreciated that the second O-ring sealing member 262 ensures a fluid seal between the rotor housing 4 'and the bearing plate 70'.

  Furthermore, in the assembled separator 2 ′, the radially outermost circumferential edge surface 630 (forming the reference surface) of the bearing plate 70 ′ is the lower opening of the rotating body housing 4 ′. It is positioned in contact with a cylindrical inner surface 632 surrounding the end. In this way, the bearing plate 70 ′ is laterally aligned at the desired final position with respect to the rotor housing 4 ′ (see FIG. 13).

  The bearing plate 70 ′ is also provided with a central circular hole that is concentric with the rotating body housing 4 ′ in the assembled separator 2 ′. In other words, in the assembled separator 2 ′, the center of the circular center hole of the bearing plate 70 ′ is located on the center line 64 ′ of the rotating body housing 4 ′. Further, as will be particularly apparent from FIG. 34 of the accompanying drawings, the bottom bearing unit 90 'is received in the central hole of the bearing plate 70'. The outermost part of the bottom bearing unit 90 ′ in the radial direction is fixed to the bearing plate 70 ′. The innermost portion in the radial direction of the bottom bearing unit 90 is disposed adjacent to the rotation shaft 78 ', but is not fixed thereto.

  As described above, the first group of internal components also includes a housing insert 72 'that is secured to the bearing plate 70'. As in the conventional separator 2 ', the housing insert 72' functions to isolate the cleaned gas from the oil separated therefrom. The improved separator 2 ′ housing insert 72 ′ also has an outlet 150 ′ for the gas to be cleaned, which is in direct sealing connection with the cylindrical inlet portion 211 of the valve unit housing 12 ′. provide.

  The housing insert 72 'is provided as a single piece of plastic material. However, in the description of the housing insert 72 'below, the insert is a four-part, outward deflecting wall 264 having a truncated frustoconical shape, a support wall 266 having a cylindrical shape, and a truncated shape. It can be thought of as comprising an isolated roof member 268 having a frustoconical shape and an outlet portion 270 defining the insert outlet 150 '(see particularly FIGS. 27 and 28).

  The isolated roof member 268 of the housing insert 72 ′ has a truncated frustoconical shape and is supported on a support wall 266. The isolated roof member 268 is provided with a central circular hole having a center line concentric with the center line 64 ′ of the rotating body housing 4 ′ in the assembled separator 2 ′. An elongated path / recess 272 (see FIG. 28) is provided in the upper surface of the isolated roof member 268. The path / recess 272 extends from the inlet 282 of the recess 272 to the outlet portion 270 having the (tubular shape) of the housing insert 72 ′, a fluid passage for the cleaned gas. Is stipulated. The inlet 282 is defined by the recessed circumferential portion of the upper circular periphery 274 of the isolated roof member 268. The inlet 282 is disposed on a substantially diametrically opposite side of the outlet portion 270 of the housing insert 72 '. The aforementioned recessed portion of the peripheral edge 274 extends through an approximately 80 ° arc 280 centered on the centerline of the housing insert hole. In an alternative embodiment, the inlet to the fluid passageway is defined by a recessed portion in the peripheral edge 274 that extends through different arcs, for example between 45 ° and 110 °. good. In the assembled separator 2 ', only a small distance separates the isolated roof member 268 from the end plate 86'. As a result, the majority of the cleaned gas entering the basin 606 between the isolated roof member 268 and the end plate 86 'is only a relatively small percentage of the cleaned gas into the region. Passing through the space between the aforementioned recessed portion of the peripheral edge 274 and the end plate 86 '.

  Thus, the space between the circumferential edge 274 and the end plate 86 ′ provides an inlet 610 to the region 606 between the isolated roof member 268 and the end plate 86 ′, but this inlet 610 has a One longitudinal portion 612 (ie, the inlet 282 to the path / recess 272) has a greater depth 613 (ie, between the peripheral edge 274 and the end plate 86 ') than the other longitudinal portions of the inlet 610. A large percentage of the cleaned gas flowing into the region 606 passes through the longitudinal portion 612 having a greater depth 613. The depth of the remaining longitudinal portion of the region inlet (610) is minimal to minimize fluid flow therethrough and thereby also minimizes the passage of oil droplets therethrough. The depth of the remaining longitudinal portion can be between 1/10 and 1/2 of the greater depth 613 and is preferably 1/3 of the greater depth 613.

  During use of the separator 2 ', the cleaned gas present in the separation disk stack 84' flows downward by a helical rotational movement along the inner surface of the cylindrical wall of the rotor housing 4 '. Thus, the cleaned gas entering the region 66 described above between the isolated roof member 268 and the end plate 86 'performs a rotational swirl motion centered on the centerline 64' of the rotor housing 4 '. . However, the gas flow entering the region 606 via the inlet 282 is immediately guided toward the insert outlet 150 ′ by the side walls 276, 278 of the elongated recess 272. This guidance of the flow of gas being cleaned will also immediately reduce the rotational swirl motion of the gas being cleaned by the inflow of gas into the elongated recess 272 via the recess inlet 282. It is believed. In this regard, from FIG. 8 of the accompanying drawings, the upstream portion of the elongated recess 272 is curved (the sidewalls 276, 278 of the recess 272 are thereby aligned with the swirling inlet fluid so that the fluid is first exposed to the sidewalls. Can be seen to substantially minimize undesirable pressure loss when impacting 276,278), and in turn, to enhance the fluid downstream along the recess 272 toward the insert outlet 150 '. The immediate reduction in swirl motion in the majority of the cleaned gas that enters the region between the isolated roof member 268 and the end plate 86 'is compared to the separator 2 described above, compared to the conventional separator 2 described above. It is believed that the pressure loss in the fluid flowing through this part of ′ is greatly reduced.

  The purged gas that does not flow through the inlet 282 and enters the region between the isolated roof member 268 and the end plate 86 ′ at other locations along the periphery of the isolated roof member 268 is an elongated recess 272. It is believed that it flows through the region with a swirl motion until it is received by, in particular, the radially outer side wall 276 guides fluid toward the insert outlet 150 'and also reduces the swirl motion of the fluid. .

  The cylindrical support wall 266 is disposed concentrically with the central circular hole in the isolated roof member 268 and protrudes downward from the underside of the isolated roof member 268. The diameter of the support wall 266 is smaller than the diameter of the peripheral edge 274 of the isolated roof member 268. In the assembled separator 2 ′, a circular edge 450 (see FIG. 27) facing below the support wall 266 below abuts the bearing plate 70 ′ at their intersection. The support wall 266 thereby supports the isolated roof member 268 on the bearing plate 70 'and ensures the correct centerline placement of the isolated roof member 268 relative to the bearing plate 70'. The support wall 266 is also provided with a plurality of cylindrical bosses 452 each having a recess for screwing and receiving the fixing member 74 ′. In the assembled separator 2 ′, each fixing member 74 ′ extends into one of the bosses 452 from below the bearing plate 70 ′ through a hole in the bearing plate 70 ′. In this way, the insert housing 72 'is fixed to the bearing plate 70'.

  The circular edge 450 facing below and below the support wall 266 is provided with a plurality of holes / recesses 454 located at various positions along the edge 450. In particular, as can be seen from FIGS. 27 and 34, the recess 454 is between the support wall 266 and the bearing plate 70 ′ through which fluid can flow during use of the assembled separator 2 ′. Provide space. In particular, during use of the separator 2 ′, the separated oil flowing radially inward from the cylindrical wall of the rotor housing 4 ′ along the bearing plate 70 ′ has a plurality of recesses. Pass 454. A percentage of the gas being cleaned also flows radially inward across the upper surface of the bearing plate 70 ′ (as will be understood by those skilled in the art) and this fluid also passes through the plurality of recesses 454. Then flow. This flow of fluid is indicated by arrow 188 'in FIG.

  An outward deflecting wall 264 extends downward from the peripheral edge 274 of the isolated roof member 268. The baffle wall 264 has a truncated frustoconical shape that diverges in the downward direction from the isolated roof member 268 toward the bearing plate 70 ′ in the assembled separator 2 ′. The diameter of the baffle wall 264 at its upper end (and thus the diameter of the peripheral edge 274 of the isolated roof member 268) is substantially equal to the outer diameter of the separating disk stack 84 '. Thanks to the truncated frustoconical shape of the baffle wall 264, the baffle wall 264 converges on the substantially cylindrical surface of the rotator housing 4 'when moving in the downward direction. The cross-sectional area of the flow path between the baffle wall 264 and the rotator housing 4 'is thus reduced in the direction of flow (ie in the downward direction). The lower free end 608 of the baffle wall 264 is spaced apart from the generally cylindrical wall of the rotator housing 4 'and on the bearing plate 70' between 2 and 200 millimeters, and preferably 14 millimeters. 456. This separation of the outer deflector wall 264 from the rotor housing 4 ′ and the bearing plate 70 ′ is separated from the oil (or other separated material) and (not in the first zone inlet 610). The gas being cleaned passes through the baffle plate 464 downwards (including its free end) radially along the cylindrical wall of the rotor housing 4 'and along the bearing plate 70'. Is allowed to do. By doing so, separated oil and cleaned gas flow through the second region 614 on the opposite side of the housing insert 72 ′ to the first flow region 606.

  Further, due to the truncated truncated cone shape, the outward deflecting wall 464 converges from the cylindrical support wall 266 when moving downward. The outward deflector wall, the isolated roof member 268, and the cylindrical support wall 266 define a generally ring-shaped cavity 458 (see FIG. 34) with an open lower end. This configuration reduces the tendency of the separated oil to flow downwardly through the inlet 282 of the recess 272 along the rotor housing 4 ', and substantially only flows upward due to fluid recirculation. Thereby reducing contamination of the gas flowing into the inlet 282 and being cleaned.

  More specifically, the relatively large space between the rotating body housing 4 ′ and the upper end of the baffle wall 264 allows for easy entry of the separated oil between these configurations and allows free downward movement of the baffle wall 264. The relatively small space between these configurations at the ends reduces the ease with which the separated oil jumps upward or recirculates between the free end and the rotor housing 4 '. In addition, any recirculation of fluid adjacent to the radially outer periphery of the bearing plate 70 ′ results in the separated oil flowing into the cavity 458 described above. For example, the oil being separated is upward along the radially outer surface of the cylindrical support wall 266, outward along the underside of the isolated roof member 268, and then the radially inner surface of the baffle wall 264. It can flow down along. Over time, the oil falls from the cavity 458 onto the bearing plate 70 'under the action of gravity. This recirculation flow path allows oil that has been separated to flow upwards to be a risk of contamination of the cleaned gas flowing into the region between the isolated roof member 268 and the end plate 86 '. No result. Thus, once cleaned, the gas flows through the region 606 inlet (ie, the inlet between the isolated roof member 268 and the end plate 86 ') toward the bearing plate 70' and upstream toward the inlet. Any subsequent recirculation of the gas returning results in the recirculated gas (and the oil droplets carried thereby) being prevented from entering the region 606 by the deflecting wall 264, causing the recirculated gas to Effectively isolate from the inlet (ie, maintain separation).

  The outlet portion 270 of the housing insert 72 'opens and supports on the upper surface of the isolated roof member 268 (more specifically, opens into the recess 272 for the gas being cleaned). It is provided as a cylindrical tube element that passes through the wall 266 and the outward deflecting wall 264 and extends in a generally radially outward direction. As will be particularly apparent from FIGS. 13 and 14 of the accompanying drawings, the outlet portion 270 is located above the lower facing edge of the support wall 266. Thus, in the assembled separator 2 ′, the outlet portion 270 is positioned above the bearing plate 70 ′, so that fluid can flow near the outlet portion 270. Preferably, the separated oil can flow near the outlet portion 270 and thus facilitates the clean gas flowing into the recess 272 of the housing insert 72 '. There is no tendency to climb up the outer surface of the exit portion 270 toward the outer periphery 274 of the isolated roof portion 268, which is a contaminated location. A support element 460 is provided at the free end of the outlet portion 270 which is open from the end of the recess 272 and protrudes downward from the lowest part of the free end so as to contact the bearing plate 70 '. . In this way, the support element 460 helps maintain a minimum space between the bearing plate 70 ′ and the outlet portion 270, and the bearing plate 70 ′ also provides support for the free end of the outlet portion 270. Allow that.

  During assembly, separator 2 'is secured to a turbine vessel (not shown) in the same manner as described above for conventional separator 2'. In particular, the improved separator 2 ′ has four threaded fastening members each passing through a different one of the four bosses 284 integrated with the lower end of the rotor housing 4. (Not shown) is secured to the turbine vessel (see especially FIGS. 18 and 29).

  As in the case of the conventional separator 2, the bearing plate 70 ′ (and therefore all of the first and second group of components) is used when the rotor housing 4 ′ and the turbine vessel are secured together. Is fixed at a desired position with respect to the rotating body housing 4 ′ by pushing the bearing plate 70 ′ into contact with the shoulder 148 ′ facing downward. The bearing plate 70 ′ is substantially sandwiched between the rotating body housing 4 ′ and the turbine vessel 178 ′ by a screw fixing member extending through the four bosses 284. The threaded fastening member is tightened and the bearing plate 70 'is consequently abutted against the shoulder 148' so that the O-ring sealing member 262 in the shoulder 148 'is pushed into the corresponding recess 260. The second helical compression spring 130 'is compressed by the top bearing unit 50'.

  During operation of the improved separator 2 ', a nozzle (not shown) in the turbine vessel directs oil injection onto the turbine wheel 136' and points the turbine wheel to arrow 134 '(see FIGS. 29 and 34). ) Rotate in the direction indicated by This rotation of the turbine wheel drives the rotation of the rotating assembly as a whole in the direction of the arrow 134 'around the center line 64' of the rotating body housing 4 '. In other words, the rotating shaft 78 ′, the upper rotating disk 80 ′, the stack 84 ′ of the separation disks 82 ′, the fan disk 240, the end plate 86 ′, the splash guard disk 242. The combined fan and turbine unit 88 '(ie, collectively referred to herein as a rotating assembly) is disposed within the rotating body housing 4' within the housing 4 'and bearing plate 70', housing insert. 72 ′ and the turbine vessel rotate together as an integral assembly.

  Gas discharged from the engine container and requiring treatment by the separator 2 'is introduced into the separator 2' via a fluid inlet 8 'located at the top of the rotor housing 4'. As indicated by arrow 68 'in FIG. 34, the inlet gas enters the rotator housing 4' in a direction parallel to the center line 64 'and enters the rotator housing 4' and the upper rotating disk 80 '. Flows through the three elongated holes 66 'in the top bearing unit 50' before passing through the twelve spokes 116 'and into the inlet 600 of the rotating assembly. The rotational movement of the twelve spokes 116 'also results in the lateral movement of the fluid disposed between the spokes, where the fluid moves in a tangential direction from the circular path of the spokes 116' and rotates. It is efficiently thrown out toward the cylindrical wall of the body housing 4. In essence, the twelve spokes 116 'impart cylindrical movement on the inlet gas.

  As the inlet gas flows downwardly through the spokes 116 ', 126' of the upper rotating disc 80 'and the separating disc 82', the gas is separated adjacently as indicated by arrow 184 'in FIG. It is moved laterally toward the cylindrical wall of the rotating body housing 4 ′ via the space 602 between the disks 82 ′. By flowing through this passage, the direction of fluid flow is changed to 90 ° or more.

  It will be appreciated that the space 604 between the radially outermost peripheries of adjacent separating discs 82 'collectively provides an exit from the rotating assembly.

  It is also well known in the art that the oil droplets 186 ′ gather together and form larger droplets as they move across the separation disk and are thrown onto the cylindrical wall of the rotor housing 4 ′. To be understood by those who are. Once received by the cylindrical wall, the oil drop 186 'travels down on the bearing plate 70' under the action of gravity. The outermost periphery of the separator stack 84 ′ is sufficiently inward from the cylindrical wall of the rotor housing 4 ′, and oil droplets are not obstructed downward on the bearing plate 70 ′. Allow to run. The O-ring sealing member 262 ensures that no oil droplets can flow between the bearing plate 70 'and the rotating body housing 4'.

  Thanks to the rotational movement of the rotating assembly, the fluid pressure in the rotating body housing 4 ′ is at the periphery of the separation disk stack 84 ′ and the bearing plate 70 ′, the support wall 266 of the housing insert 72 ′ and the roof member 268 and It is understood by those skilled in the art that it is greater than in the area surrounded by the bearing plate 70 '. As a result, there is a tendency for the gas flow to be cleaned downward along the cylindrical wall of the rotator housing 4 ′ and radially inward along the bearing plate 70 ′. This fluid flow causes the separated oil droplets to move downward along the cylindrical wall onto the lower bearing plate 70 and then through the holes in the support wall 266 of the housing insert 72 '. There is a tendency to push radially inward along 70 '. This gas fluid flow is indicated by arrow 188 '(see FIG. 34). The gas fluid flow moves radially inward across the upper surface of the bearing plate 70 'toward the central circular hole in the housing insert 72'. This flow across the bearing plate 70 'tends to push the separated oil droplets across the bearing plate 70 toward the bottom bearing unit 90', through which the oil droplets pass. The combined fan and rotating fan blades 140 ′ of the turbine unit 88 ′ are in the turbine vessel in the region of the bottom bearing unit 90 ′ (where the rotor housing 4 ′ is attached during use). It tends to reduce the static pressure of the oil and draws oil droplets through the bottom bearing unit 90 '. The fan blades 140 'can then throw the oil droplets radially outward into the turbine vessel, from where they can be returned to the engine crankcase. During this time, the gasified fluid flowing across the bearing plate 70 ′ is drawn upward through the central hole in the insert housing 72 ′, and the end plate 86 ′ and the fan disc 240 Passes radially outward between. The gasified fluid then exits the rotating body housing 4 'by flowing through the cylindrical portion 211 of the valve unit housing 12', which is sealingly connected to the housing insert 72 ', and is inserted into the housing. It passes through the body outlet 150 'and the rotating body housing 10'.

  Some of the gas that is being cleaned while flowing over the upper surface of the bearing plate 70 ′ and in the support wall 266 of the housing insert 72 ′ is below the end plate 86 ′ and the housing insert 72. It flows to the cylindrical portion 211 via an alternative path between the upper side of the 'isolated roof member 268. This alternative path is indicated by arrow 190 '.

  As in the conventional separator 2, the oil flow through the bottom bearing unit 90 'of the improved separator 2' has a beneficial lubricating effect on the bearing unit. The top bearing unit 50 'occurs naturally in the turbine vessel and is transported upward to the top bearing unit 50' via a longitudinal flow path 92 'extending through the rotating shaft 78'. It is similarly lubricated by oil mist.

  Either the conventional ALFEDEX ™ separator 2 or the improved separator 2 ′ described above is an alternative for rotating the rotating shaft 78 ′ as shown in FIG. 35 of the accompanying drawings. Can be incorporated. Referring to FIG. 35, it can be seen that the previously described Pelton wheel has been replaced by a brushless electric motor 380, whose rotor 382 has a rotating shaft 78 ″ below the bearing plate 70 ′. It is fixed to the lower end of. The electric motor 380 is shown in FIG. 35 by driving a conventional ALFEDEX ™ separator 2. However, as will be appreciated by those skilled in the art, the electric motor drive structure shown in FIG. 35 is also used in connection with the improved separator 2 'described above. Rukoto can.

  Referring to FIG. 35, the electric motor 380 having the electric motor driving structure is fixed to the rotating body housing 4 ′ by a plurality of screw screw fixing members 180 ′ (only one of which is shown in FIG. 35). The housing 384 is disposed. The motor housing 384 includes upper and lower portions 386, 388 that are secured together by suitable securing means with an O-ring sealing member 390 located at the interface between them. O-ring seal 390 prevents unwanted leakage of dust, water, and / or other foreign matter located outside housing 384 into the space within housing 384. In this way, electronic components (including printed wiring boards and / or other circuit components) are isolated from materials that can result in their damage and subsequent failure.

  The upper portion 386 of the housing 384 is provided with a cylindrical wall 392 projecting downward defining a central hole in the upper portion 386. The cylindrical wall 392 is arranged so as to be concentric with the rotary shaft 78 ″ in the assembled separator. A baffle washer 139 ″ is held on a rotating shaft 78 ″ by a circlip 404 ″. The deflector washer 139 ″ thereby pushes upward against the radially inner bearing race of the bottom bearing unit, as in a conventional ALFEDEX ™ separator 2. The baffle washer 139 ″ has a radially outward rim radially away from the cylindrical wall 392 and allows the passage of contaminated oil therebetween.

  The upper end of yet another portion 394 of the motor housing 384 (having a generally truncated frustoconical shape) is disposed and sealed at the lower end of the cylindrical wall 392 of the upper portion 386. The seal between the cylindrical wall 392 and the truncated frustoconical portion 394 defines a closed loop shape and is provided by a further O-ring sealing member 396. The lower end of the truncated frustoconical portion 394 (having a larger diameter than its upper end) is also sealed to the lower portion 388 of the motor housing 384 by a further O-ring sealing member 398. This seal also defines a closed loop shape.

  Accordingly, on one side of the truncated truncated cone portion 394, the portion 394 and the lower portion 388 are thereby arranged therein with the electric motor 380 disposed therein and the lower end of the rotating shaft 78 ″ extends therein. To form a space. On the other side of the truncated frustoconical part 394, the remaining part of the part 394 and the upper part 386 and the lower part 388 have an electronic / electrical configuration for supplying power and control signals to the electric motor 380 therein. An element (eg, printed wiring board 408) is disposed to form a space / partition 406 that is totally closed and sealed. The partitioned portion 406 is sealed not only from the outside of the motor housing 384 but also from the space in which the electric motor 380 is disposed. Contaminated oil flowing through this space during use of the separator is therefore prevented from accessing the electronic / electrical components and causing damage to them.

  Further, the truncated frustoconical portion 394 extends therethrough a wire 410 (which connects the motor 380 and the electrical supply / control component) to which the wire is sealed. Not shown).

  One or more electrical connectors 412 also extend through holes 414 in the motor housing 384 and are located external to the separator (eg, corresponding to the vehicle in which the separator is used). A line (not shown) is allowed to connect to the electrical supply / control component stored in the partitioned portion 406. In other words, the electric wire is provided with a plug for mechanically and electrically connecting to the connector 412. The wires can carry power and / or control signals for the electric motor drive structure. The connector 412 is sealed to the housing 384 and prevents unwanted entry of foreign objects into the partitioned portion 406.

  Although the partitioned portion 406 has a generally annular shape that is concentric with the rotating assembly of the separator, it will be understood that the partitioned portion 406 can have a different shape.

  The stator 400 of the electric motor 380 is fixed to the lower portion 388 of the motor housing 384. The radially inner portion of the truncated frustoconical portion 394 sealing with the cylindrical wall 392 has a hole having a diameter substantially equal to the innermost diameter of the stator 400 of the electric motor 380. It prescribes.

  During use of the separator provided with the electric motor drive structure of FIG. 35, the electricity supply is connected to the brushless electric motor 380 to rotate its rotor 382 and thereby rotate the rotating shaft 78 ″. Let As explained above, the separated oil passes down from the rotor housing 4 through the bottom bearing unit 90. In the separator provided with the electric motor drive structure of FIG. 35, this separated oil is discharged from the bottom bearing unit into the motor housing 384, and more specifically the cylindrical shape of the upper housing portion 386. It is discharged into the space in the wall 392. The separated oil then passes through the rotor 380 of the electric motor 380 and exits the motor housing 384 through a small hole 402 located adjacent to the electric motor 380 in the lower housing portion 388. The oil passing through the rotor 382 (or through the space between the rotor 382 and the stator 400) and coming into contact with the rotor 382 and the stator 400 causes the electric wire of the stator 400 to be epoxy lacquer. Since it is covered with a layer of (epoxy lacquer), the operation of the electric motor 380 is not adversely affected.

  Reference is now made to FIGS. 37 to 41 of the accompanying drawings for the manufacture of an improved separator 2 ′, and in particular for the assembly of the top bearing unit 50 ′ with respect to the rotor housing 4 ′. These figures show the top bearing relative to the rotor housing 4 'in a position that is axially aligned with the bottom bearing unit 90' when the bearing plate 70 'is assembled against the lower shoulder 148' of the rotor housing 4 '. The process for spin welding the unit 50 'is shown. The assembly process ensures the axial alignment of the top and bottom bearing units 50 ', 90' despite the shape variation resulting from the deflection of the housing 4 'following injection molding of the rotating body housing 4'.

  The process uses a spin welding jig 500 that includes a stator part 502 and a rotor part 504 that is rotatably provided to the stator part 502. The stator portion 502 includes a circular disc 506 having a diameter equal to that of the bearing plate 70 ′. The shape of the circular disk 506 allows the circular disk 506 to be positioned in contact with the rotating body housing 4 ′ in the same manner as the bearing plate 70 ′ in the assembled separator 2 ′. It seems. The rotor portion 504 includes a shaft 508 that extends through the center of the circular disc 506 and is oriented at right angles to the circular disc 506. The shaft 504 is provided to the circular disc 506 by a bearing assembly (not shown).

  One end of the shaft 508 is provided with a head 510 for receiving the top bearing unit 50 '. The head 510 is provided as a circular disk concentric with the circular disk 506 of the fixed body part 502, and the center is placed on the center line around which the rotor part 504 rotates. The diameter of the head 510 is substantially equal to the diameter of the radially inner surface of the cylindrical wall 58 'projecting below the top bearing unit 50'. In this way, the cylindrical wall 58 ′ of the top bearing unit 50 ′ is around the head 510 with little or no relative lateral movement between the top bearing unit 50 ′ and the shaft 508. Can be placed. Relative rotational movement between the top bearing unit 50 ′ and the shaft 508 is prevented by a protrusion 512 rising from the circular disc of the head 510. The head 510 includes three protrusions 512 that are independent from each other and are equally spaced around the rotation center line of the shaft 508. Each of the protrusions 512 is partially circular and is positioned and dimensioned to be disposed within the partially circular slot 66 'of the top bearing unit 50'. The protrusion 512 is substantially the same size and shape as the slot 66 'so that when the protrusion 512 is received by the slot 66 (see particularly FIGS. 37 and 38), the shaft 508 The rotational movement of the top bearing unit 50 'relative to the head 510 is substantially prevented.

  At the second end of the shaft 508 away from the end where the head 501 is provided, the rotor part 504 is connected to a motor for driving the rotational movement of the rotor part 504 relative to the stator part 502. Means 514 are provided.

  A spin welding jig 500 with a top bearing unit 50 'disposed on its head 510 is shown in Figure 39 of the accompanying drawings. By arranging the top bearing unit 50 'on the head 510, the shaft 508 and the top bearing unit 50' are inserted into the rotating body housing 4 'as shown in FIG. The circular disk 506 is disposed in contact with the lower shoulder 148 ′ of the rotating body housing 4 ′. More specifically, the radially outermost peripheral surface 634 (which forms the reference surface) of the circular disc 506 is a cylindrical inner surface 632 that surrounds the lower open end of the rotor housing 4 ′. Abut and align. In this way, the lateral positioning of the top bearing unit 50 ′ relative to the rotating body housing 4 ′ is determined. By arranging the spin welding jig 500 in the rotor housing 4 ′ in this way, the rotation center line of the rotor part 504 is the center line 64 previously described of the rotor housing 4 ′. Concentric with ´.

  The rotor portion 504 abuts a ridge 238 provided on the rotor housing 4 'from the first position where the top bearing unit 50' is away from the upper portion of the rotor housing 4 '. (See FIG. 34) The top bearing unit 50 'is movably disposed relative to the stator portion 502 so that it can move to the second position. During the assembly of the top bearing unit 50 ′ with the rotator housing 4 ′, the rotator housing 4 ′ is held stationary, and the circular disc 506 of the stator part 502 is attached to the rotator housing 4 ′. While positioned against the lower shoulder 148 ', the rotor section 504 is rotated at a relatively high speed and is further moved axially into the rotator housing 4' to rotate / spin. The rotating top bearing unit 50 ′ is brought into contact with the ridge 238. The pivoting top bearing unit 50 ′ is forced against the ridge 238 to generate frictional heat and thereby melt the abutment surfaces of the top bearing unit 50 ′ and the plastic material of the ridge 238. While the bearing unit 50 ′ is pushed against the ridge 238, the rotational movement of the shaft 508 is rapidly decelerated and stopped, causing the molten plastic material to cool and thereby causing the bearing unit 50 ′ and the ridge 238 to Are allowed to join together. The top bearing unit 50 'and the rotator housing 4' are thereby rotationally welded together.

  The rotator housing 4 ′ is stationary by a screw threaded fastening member (see FIG. 40) that extends through the boss 284 in the rotator housing 4 ′ and into the cylindrical mounting block 516 during the rotary welding process. Can be retained.

  Once the top bearing unit 50 'is secured to the rotator housing 4', the spin welding jig 500 can be removed from the rotator housing 4 '. The top bearing unit 50 'is thereby correctly positioned and secured relative to the rotor housing 4' as shown in FIG. 41 of the accompanying drawings. It will be appreciated that the top bearing unit 50 'is located at a centered position relative to the lower circular shoulder 148' of the rotating body housing 4 '. Therefore, when the internal components of the separator 2 'are arranged in the housing 4', the contact of the bearing plate 70 'with the shoulder 148' is such that the bottom bearing unit 90 'is also concentric with the shoulder 148'. Ensure that it is placed. The top and bottom bearing units 50 ', 90' are thereby axially aligned despite any previous deflection of the rotor housing 4 'following injection molding.

  The improved separator versatility when compared to the conventional separator 2 is highlighted by the advantages of certain modules / components that can be exchanged in different separator systems (see FIG. 36). ). The ability of the rotor housing 4 '(ie one particular type of module) to accept different valve units 14' (ie different types of modules) has already been described above. This modular approach is achieved by different types of modules / components of a given type (eg, valve unit 14 ') that have the same features for connection / interface with other modules / components. Has been. By way of example, the separator system is provided in different types with common features that allow it to match the rotor housing 4 'even though the valve unit can be different in many other respects. So, one of several different types of valve units can potentially be used. The table provided by FIG. 36 shows how different components / types of the separator system can be additionally provided in one component / type, or in one configuration. Indicates whether the element / type can be exchanged for a different type.

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

Claims (11)

A gas clean separator (2 ') for separating a flowable mixture of gas and liquid , said separator (2') comprising:
A housing (4 ') defining an internal space;
A rotating assembly (78 ″, 84 ′) including a rotating shaft (78 ′), an upper rotating disk (80 ′), a separated disk stack (84 ′) and an end plate (86 ′), wherein the rotation An assembly (78 ″, 84 ′) is disposed in the interior space to impart rotational motion on the mixture of materials and is rotatable about a center line (64 ′) relative to the housing (4 ′). An inlet (600) for receiving the mixture, an outlet (604) from which the liquid is discharged during use, and fluid communication between the inlet (600) and the outlet (604) A rotating assembly (78 ′, 84 ′) comprising a flow path (602) of:
With
Wherein the rotation axis (78 ') is in the separator at least one of said moiety Tsu along the length of the rotational shaft (78') of the contact portion which is slidably received components (2 ') Separator characterized in that it is provided with a coating of plastic material.   The separator of claim 1, wherein at least one of the components is of a metallic material.   The separator according to claim 1 or 2, wherein at least one of the components is a helical spring.   A separator as claimed in any one of the preceding claims, wherein at least one of the components is a bearing unit (50 ').   The rotating shaft (78 ') receives two of the components on the upper end portion and the lower end portion of the rotating shaft (78'), where the individual components are helical springs (130 ', 96'). A separator as claimed in claim 1 or 2.   Each helical spring (130 ', 96') has two bearing units (50 ') that connect the rotating assembly (78', 84 ') and rotating shaft (78') to the housing (4 '). , 90 '), wherein the helical spring (130') of the upper end portion is compressed into a top bearing unit (50 ') and the lower end portion of the helical spring (130') is compressed. The separator according to claim 5, wherein the helical spring (96 ') is compressed into the bottom bearing unit (90').   The separator according to claim 6, wherein the individual helical springs (130 ', 96') are of metallic material.   The separator according to any one of claims 1 to 7, wherein the rotating shaft (78 ') is made of an unhardened metal.   The separator according to claim 8, wherein the unhardened metal is unhardened steel.   The rotating assembly (78 ′, 84 ′) is disposed on at least one element (114 ′, 116 ′, 254) protruding from the rotating shaft (78 ′), that is, on the outer surface of the rotating shaft (78 ′). A hub (114) of the upper rotating disk (80 ') provided, and a radial extension from the hub (114) for connecting the upper rotating disk (80') to the hub (114) A plurality of spoke members 116 ′ and a plurality of splines extending radially from the hub 114 for preventing rotation of the separation disk stack about the rotation axis 78 ′. 254), wherein the element (114 ', 116', 254) is of the same material as the coating and is integrally formed therewith. In any one of 9 Mounting of the separator.   11. Separation according to claim 10, wherein the covering and the at least one element (114 ', 116', 254) are injection-molded on the axis of rotation (78 ') and thereby formed simultaneously with each other. Machine.

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