DE202021105900U1 - Housing of a turbocharger - Google Patents

Abstract

Housing (1) of a turbocharger, in particular a compressor housing of a turbocharger, comprising
a cavity (3) which is designed to receive a compressor wheel, and a cooling channel (7) which is designed such that a coolant flows through the cooling channel (7), and which has an inlet (9), an outlet (11) , comprises a first cooling channel (13) and a second cooling channel (15),
wherein the inlet (9) comprises an inlet (19), a first outlet (21) and a second outlet (23), the inlet (9) is designed such that it divides an inlet coolant flow into a first coolant flow and a second coolant flow, the first outlet (21) is in fluid communication with the first cooling channel (13) which extends at an angle from the first outlet (13), the second outlet (23) is in fluid communication with the second cooling channel (15) which extends at an angle from the second Exit (23) extends,
wherein the first cooling channel (13) through which the first coolant flows extends from the first outlet (13) to the outlet (11), the second cooling channel (15) through which the second coolant flows extends from the second outlet (23) extends to the outlet (11) so that the first and second cooling ducts (13, 15) run around the cavity (3),
wherein the outlet (11) is in fluid communication with the first and second cooling channels (13, 15).

Description

The invention relates to a housing of a turbocharger, in particular a compressor housing of a turbocharger.

Turbochargers are well known in the automotive industry. A turbocharger can be designed as an exhaust gas turbocharger. Such an exhaust gas turbocharger can be electrically assisted. Alternatively, the turbocharger can also be designed as an electrically driven turbocharger. A turbocharger can be designed as a fuel cell air supply for a fuel cell. Cooling improves the performance and mechanical durability of a turbocharger and extends its life.

One possibility of cooling is water cooling. A conventional water cooling channel which is formed in a housing of the turbocharger is in the form of a ring and is delimited by inner wall surfaces of the housing. An inlet, which is designed as a T-shaped pipe branch in the ring, and an outlet are provided for the supply and discharge of water into and out of the cooling channel. The outlet is opposite or approximately opposite the inlet. However, it is difficult to design the cooling channel so that the water is evenly distributed in order to ensure good cooling. The construction of such a conventional cooling channel requires many repetitions of the simulation in order to achieve good water distribution.

It is an object of the invention to provide a housing with an improved cooling channel. This goal is achieved by a housing of a turbocharger having the features of claim 1.

The housing of the turbocharger, in particular a compressor housing of a turbocharger, comprises a cavity, which is designed to accommodate a compressor wheel, and a cooling channel, which is designed so that a coolant flows through the cooling channel and the one inlet, one outlet, a first cooling channel and a second cooling channel. The inlet includes an inlet, a first outlet, and a second outlet. The inlet is configured to divide an inlet coolant flow into a first coolant flow and a second coolant flow. The first exit is in fluid communication with the first cooling channel that extends at an angle from the first exit. The second exit is in fluid communication with the second cooling channel that extends at an angle from the second exit. The first cooling channel, through which the first coolant flows, extends from the first outlet to the outlet, and the second cooling channel, through which the second coolant flows, extends from the second outlet to the outlet, so that the first and second cooling channels around the cavity get lost. The outlet is in fluid communication with the first and second cooling channels.

The above case provides a more efficient cooling system that ensures even distribution of the coolant.

The housing is part of the turbocharger and is used to hold and protect rotating components, in particular the compressor wheel. The turbocharger can be an exhaust gas turbocharger or an electrically assisted turbocharger with an electrically driven or assisted compressor wheel or a turbocharger for a fuel cell. The compressor wheel of the turbocharger can be arranged in the cavity of the housing in such a way that it rotates about a longitudinal axis during operation. However, other rotatable components can also be arranged in the cavity, e.g. B. a shaft connected to the compressor wheel. A housing designed as a compressor housing accommodates the compressor or at least the compressor wheel. Another housing part, which is connected to the compressor housing, can accommodate further rotating components.

The housing can be part of a turbocharger for a fuel cell. Such a turbocharger is designed as a fuel cell air supply (FCAS) with a compressor and a turbine. Similar to an internal combustion engine, the fuel cell requires compressed air in order to achieve a high power density. As an alternative to the turbocharger, compressed air for the fuel cell can be provided by an electrically driven compressor. The housing of such a compressor can have the same features as the housing described above.

The cooling channel is designed such that it dissipates heat from one or more rotating components inside the cavity, preferably the compressor wheel. Preferably, there is no heat transfer between the channels for the supply and discharge of the coolant at the inlet and at the outlet.

The cooling channel includes the inlet and the outlet through which the coolant flows in and out of the cooling channel. The cooling channel is formed by housing walls, so that at least the first and the second cooling channel are defined by inner sides of housing walls. The coolant can be water. The inlet divides the supplied coolant flow uniformly or almost uniformly into the first coolant flow and the second coolant flow. As the inlet between a channel that provides the coolant, and a main cooling surface of the housing is arranged, the supplied coolant flow is divided and passed into the first and second cooling ducts before it reaches the main cooling surface of the housing. The first cooling channel and the second cooling channel direct the coolant from the inlet to the outlet and around the cavity which is located between the first and second cooling channels, thereby cooling the main cooling surface of the housing. The first cooling channel and the second cooling channel preferably run in the form of a split ring, it being possible for the lengths of the arc of the first cooling channel and the second cooling channel between the inlet and the outlet to be different. The gap in the ring is caused by the inlet where the supplied coolant flow is divided. If the housing is designed as a compressor housing, the first cooling channel and the second cooling channel preferably run around a region of the cavity in which the compressor blades of the compressor wheel are located.

The inlet divides the supplied coolant flow. Preferably the inlet coolant flow is split into two halves. The design of the inlet is preferably symmetrical, so that the coolant is evenly distributed and the same amount of coolant flows into the first cooling channel and into the second cooling channel. In one embodiment, the flow areas of the first and the second outlet are symmetrically or almost symmetrically shaped and the same or almost the same size in order to achieve a uniform distribution of the coolant. The inlet coolant stream and the first and second coolant streams can flow in the same direction, which can be achieved through an inlet with a tubular inlet and two tubular outlets, which all extend in the same direction. An alternative embodiment can be a Y-shaped inlet in which the directions of the first coolant flow and the second coolant flow are mirror-symmetrical to the direction of the inlet coolant flow. The same or approximately the same sizes of the flow areas of the first and second outlet result in a uniform distribution of coolant. This effect is supported by the fact that a cross-sectional area of the first cooling channel and a cross-sectional area of the second cooling channel are the same or almost the same size. However, the shapes of the cross-sectional areas can be different.

In one embodiment, the flow areas of the first outlet and the second outlet are half as large or less than half as large as a flow area of the inlet, which supports an even distribution of water. The cross sections of the first and second cooling channels are preferably half as large or less than half as large as the cross section of the inlet or of an inlet channel which supplies the coolant to the inlet. An enlargement of the cross-sections to more than half the cross-section of the inlet leads to the cooling channel being less efficient and a uniform distribution of the coolant not being guaranteed. However, such a construction would still be better than the traditional approach.

In one embodiment, the first cooling channel and the second cooling channel are arranged in a plane perpendicular to the longitudinal axis. The first cooling channel and the second cooling channel can each run in the form of an arc, so that the first cooling channel and the second cooling channel form a split ring. The arches do not have to be the same length. When the outlet is opposite the inlet, the arcs are the same length. If the arcs are of different lengths, the outlet will be in a position on the split ring closer to one of the outlets. The outlet can be placed in any position depending on the customer's requirements for the housing. The asymmetrical positioning of the outlet and the inlet offers further degrees of freedom in the design of the cooling channel.

The inlet preferably runs perpendicular to the first and second cooling ducts, but the inlet does not have to run parallel to the longitudinal axis. This arrangement avoids an asymmetrical flow in the first and second cooling ducts, which could impair an even distribution of water. In one embodiment, the entrance extends parallel to the longitudinal axis, which enables a compact design.

The housing with the cooling channel described above offers a high degree of freedom in the positioning of the inlet and the outlet and at the same time ensures an even distribution of water for good cooling. In addition, fewer simulation iterations are required to achieve good water distribution, which means less effort for the design of the cooling channel in the housing.

• 1 zeigt eine Schnittansicht eines Ausführungsbeispiels eines Turboladergehäuses und eine Schnittansicht eines Ausführungsbeispiels eines Kühlungskanals in dem Gehäuse.
• 2 zeigt eine dreidimensionale Ansicht eines Ausführungsbeispiels eines Kühlungskanals.
• 3 zeigt eine detaillierte Vorderansicht eines Bereichs des Kühlungskanals.
• 4 zeigt eine Schnittdarstellung des Kühlungskanals.
• 5 zeigt eine dreidimensionale Ansicht eines weiteren Ausführungsbeispiels eines Kühlungskanals.
• 6 zeigt eine dreidimensionale Ansicht eines weiteren Ausführungsbeispiels eines Kühlungskanals.

In the following, some exemplary embodiments are explained in more detail with reference to the drawing.

• 1 FIG. 11 shows a sectional view of an exemplary embodiment of a turbocharger housing and a sectional view of an exemplary embodiment of a cooling channel in the housing.
• 2 shows a three-dimensional view of an embodiment of a cooling channel.
• 3 Figure 11 shows a detailed front view of a portion of the cooling channel.
• 4th shows a sectional view of the cooling channel.
• 5 shows a three-dimensional view of a further exemplary embodiment of a cooling channel.
• 6th shows a three-dimensional view of a further exemplary embodiment of a cooling channel.

Identical or functionally equivalent components are provided with the same reference symbols in the figures.

1 shows a sectional view of an embodiment of a housing 1 a turbocharger, which is designed as a compressor housing. The case 1 has a cavity 3 on, the one for receiving a about a longitudinal axis 5 rotatable compressor wheel (in 1 not shown) is formed. Around the cavity 3 is a volute section 6th arranged. The compressor draws air in axially and compresses it, with the air flowing through the volute section 6th flows. The compressed air is then fed to an engine. In an alternative embodiment, the air is fed to a fuel cell.

There is a cooling channel in the housing 7th formed through which a coolant flows and through wall surfaces of the housing 1 is limited. The coolant is water. The cooling duct 7th is between the cavity 3 and the volute section 6th and around a portion of the cavity 3 arranged in which there are compressor blades of the compressor wheel when the compressor wheel is in the cavity 3 is mounted.

Illustrative shows 1 also a sectional view of the cooling channel 7th which is limited by the inside of the housing walls.

2 shows a three-dimensional view of an embodiment of a cooling channel 7th . The case 1 is not shown, only surfaces of the housing walls that form the cooling duct 7th define.

The cooling duct 7th includes an inlet 9 , an outlet 11 , a first cooling channel 13th and a second cooling channel 15th . A U-shaped tube 17th is with the inlet 9 connected so that there is a fluid connection between the components. The inlet 9 has an entrance 19th , a first exit 21 and a second exit 23 . The entrance 19th is in fluid communication with the tube 17th through which the coolant enters the inlet 9 flows. The inlet 9 is designed to have an inlet coolant flow passing through the tube 17th is provided, divided into a first coolant flow and a second coolant flow coming from the first outlet 21 or from the second exit 23 flow away. In the in 2 shown embodiment of the inlet 9 is the entrance 19th designed so that the inlet coolant flow and the first coolant flow and the second coolant flow flow in the same direction, which is parallel to the longitudinal axis 5 is.

The first exit 21 is in fluid communication with the first cooling channel 13th that is perpendicular to the first exit 21 extends. The second exit 23 is in fluid communication with the second cooling channel 15th that is perpendicular to the second exit 23 extends. The first and the second cooling channel 13th , 15th run in a plane perpendicular to the longitudinal axis 5 and form a split ring, the gap being between the first and second output 21 , 23 of the inlet 9 is located. The outlet 11 is opposite the inlet 9 and extends in the same direction as the inlet 9 . The outlet 11 is in fluid communication with the first and second cooling passages 13th , 15th . The first coolant stream thus flows from the first outlet 21 through the first cooling channel 13th to the outlet 11 . The second coolant stream flows from the second outlet 23 through the second cooling channel 15th to the outlet 11 . The outlet 9 is in fluid communication with another pipe 25th (in 2 not shown), through which the coolant from the cooling channel 7th flows.

Sizes of the flow areas of the first and second cooling channels 13th , 15th correspond to the cross-sectional areas of the first and second cooling channels 13th , 15th . Their sizes along the respective arches are the same or almost the same. However, their shapes can vary along their respective arcs depending on the case design and cooling needs.

3 Figure 10 shows a detailed front view of the inlet 9 and portions of the first and second cooling channels 13th , 15th in fluid communication with the first and second outputs, respectively 21 , 23 stand. The inlet 9 has a tubular entrance 19th and two tubular outlets 21 , 23 that all extend in the same direction, so that's through the inlet 9 flowing coolant is only divided into the first and second coolant flow, but does not change its direction of flow. The transition to the first and second exit 21 , 23 is arched. Hence the inlet can be called a split pad. A size of the inlet flow area 19th is A. The first and the second output 21 , 23 are perpendicular to the first and second cooling ducts 13th , 15th arranged, which leads to changes in direction of the first and second coolant flows when these in the first and second cooling ducts 13th , 15th enter. Through the inlet 9 , the one between the pipe serving as the water inlet channel 17th and a main cooling surface of the housing is arranged, the inlet coolant flow is divided and into the first and second cooling channels 13th , 15th before it reaches a main cooling surface of the housing.

4th FIG. 14 shows a sectional view along the line BB from FIG 3 . The shapes of the first and second exits 21 , 23 and their flow areas are symmetrical or at least nearly symmetrical. The size of the flow area of the first and second outlet 21 , 23 each is A / 2, which is half the size of the flow area A of the inlet 19th equals, or nearly A / 2. Such an inlet 9 ensures even water distribution, with the inlet coolant flow being split into halves due to the symmetrical or nearly symmetrical design of the outlets 21 , 23 symmetrically in the first and second cooling duct 13th , 15th be directed. This effect is supported by the fact that the first and second cooling ducts 13th , 15th have the same or almost the same flow area sizes along the respective bends. Nevertheless, the shapes of the flow areas can vary along their respective arcs, as in FIG 4th shown in the first cooling channel 13th has a protruding edge portion.

5 shows a three-dimensional view of a further exemplary embodiment of a cooling channel 7th . The following description focuses on the differences from the previous exemplary embodiment.

The outlet 11 is not opposite the inlet 9 but is located at a position on the split ring that is closer to one of the first and second exits 21 , 23 lies, whereby a first and second cooling channel 13th , 15th with different arc lengths. In this exemplary embodiment, the second cooling channel is 15th about three times as long as the first cooling channel 13th . However, the first and second cooling channels run 13th , 15th in a plane perpendicular to the longitudinal axis 5 and also form a split ring. 5 shows that the cross-sectional areas 14th , 16 the first and the second cooling channel 13th , 15th are different and vary along their respective arcs, but the sizes remain the same or nearly the same.

Although the positions of the inlet 9 and the outlet 11 cause the first and second cooling ducts 13th , 15th are of different lengths, takes care of the entrance 9 nevertheless for an even water distribution. The inlet 9 divides the supplied coolant flow into two halves. Such an inlet 9 offers the possibility of the outlet 11 at any point of the first and second cooling ducts 13th , 15th to arrange formed split ring. The outlet 11 however, it does not have to be perpendicular to the longitudinal axis or to the first and second cooling ducts 13th , 15th get lost.

6th shows a three-dimensional view of a further exemplary embodiment of a cooling channel 7th . The following description focuses on the differences from the previous embodiments.

The inlet 9 does not run parallel to the longitudinal axis 5 but at an angle. Still the inlet is 9 perpendicular to the first and second cooling channel 13th , 15th arranged so that the first and second output 21 , 23 are designed symmetrically or almost symmetrically, which ensures an even distribution of water. The sizes of the flow areas 22nd , 24 of the first and second output 21 , 23 are the same or nearly the same.

The asymmetrical arrangement of the inlet 9 and the outlet 11 while at the same time evenly distributing the water, it is possible to design a housing with many degrees of freedom in order to achieve good cooling.

The features described above and in the claims and those shown in the drawings can advantageously be implemented both individually and in various combinations. The invention is not restricted to the examples described, but can be modified in many ways within the scope of specialist knowledge.

List of reference symbols

1

casing

3

cavity

5

Longitudinal axis

6th

Volute casing section

7th

Cooling duct

9

inlet

11th

Outlet

13th

first cooling channel

14th

first cross-sectional area

15th

second cooling channel

16

second cross-sectional area

17th

pipe

19th

input

21

first exit

22nd

first flow area

23

second exit

24

second flow area

25th

another pipe

Claims (14)

Housing (1) of a turbocharger, in particular a compressor housing of a turbocharger, comprising a cavity (3) which is designed to receive a compressor wheel, and a cooling channel (7) which is designed so that a coolant flows through the cooling channel (7), and which has an inlet (9), an outlet (11) , comprises a first cooling channel (13) and a second cooling channel (15), wherein the inlet (9) comprises an inlet (19), a first outlet (21) and a second outlet (23), the inlet (9) is designed such that it divides an inlet coolant flow into a first coolant flow and a second coolant flow, the first outlet (21) is in fluid communication with the first cooling channel (13) which extends at an angle from the first outlet (13), the second outlet (23) is in fluid communication with the second cooling channel (15) which extends at an angle from the second Exit (23) extends, wherein the first cooling channel (13) through which the first coolant flows extends from the first outlet (13) to the outlet (11), the second cooling channel (15) through which the second coolant flows extends from the second outlet (23) extends to the outlet (11) so that the first and second cooling ducts (13, 15) run around the cavity (3), wherein the outlet (11) is in fluid communication with the first and second cooling channels (13, 15). Housing (1) Claim 1 , wherein the inlet (9) is designed such that it divides the inlet coolant flow uniformly or almost uniformly into the first coolant flow and the second coolant flow. Housing (1) Claim 1 or 2 , wherein the flow areas (22, 24) of the first outlet (21) and the second outlet (23) are the same or almost the same size and are preferably symmetrical or almost symmetrical in shape. Housing (1) according to one of the preceding claims, wherein the flow areas (22, 24) of the first outlet (21) and the second outlet (23) are half as large or less than half as large as a flow area of the inlet (19). Housing (1) according to one of the preceding claims, wherein a cross-sectional area (14) of the first cooling channel (13) and a cross-sectional area (16) of the second cooling channel (15) have the same or almost the same size. Housing (1) according to one of the preceding claims, wherein the first cooling channel (13) and the second cooling channel (15) are arranged in a plane perpendicular to a longitudinal axis (5), the compressor wheel being rotatable about the longitudinal axis (5). Housing (1) according to one of the preceding claims, wherein the first cooling channel (13) and the second cooling channel (15) each run in an arc shape so that the first cooling channel (13) and the second cooling channel (15) form a split ring. Housing (1) according to one of the preceding claims, wherein the inlet (9) extends perpendicular to the first and second cooling ducts (13, 15). Housing (1) according to one of the Claims 6 until 8th , wherein the input (9) runs parallel to the longitudinal axis (5). Housing (1) according to one of the preceding claims, wherein the inlet (9) is designed so that the inlet coolant flow and the first coolant flow and the second coolant flow flow in the same direction of flow. Housing (1) according to one of the preceding claims, wherein the housing (1) is designed as a compressor housing. Housing (1) Claim 11 wherein the first and second cooling ducts (13, 15) extend around a region of the cavity (3) in which the compressor blades of the compressor wheel are located when the compressor wheel is received in the interior of the cavity (3). Housing (1) according to one of the preceding claims, which is designed as a fuel cell air supply housing for a fuel cell, in particular as a compressor housing of the fuel cell air supply housing. Compressor housing (1) of a fuel cell comprising a cavity (3) which is designed to accommodate a compressor wheel, and a cooling channel (7) which is designed so that a coolant flows through the cooling channel (7), and which has an inlet (9 ), an outlet (11), a first cooling channel (13) and a second cooling channel (15), the inlet (9) comprising an inlet (19), a first outlet (21) and a second outlet (23), the inlet (9) is configured to divide an inlet coolant flow into a first coolant flow and a second coolant flow; the first outlet (21) is in fluid communication with the first cooling channel (13) which extends at an angle from the first outlet (13) , the second outlet (23) in fluid communication with the second cooling channel (15) which extends at an angle from the second outlet (23), the first cooling channel (13) through which the first coolant flows extending from the first outlet (13) to the outlet (11), the second cooling channel (15) through which the second coolant flows, extends from the second outlet (23) to the outlet (11) so that the first and second cooling channels (13, 15) extend around the cavity (3), the outlet (11) in fluid communication with the first and second cooling ducts (13, 15).

Images