KR20140109313A - Liquid-cooled rotary electric machine having cooling jacket with bi-directional flow - Google Patents

Abstract

A liquid-cooled rotary electric machine includes a jacket defining a heat transfer surface and a sleeve defining a coolant accommodating surface. A fluid channel having an entry and an exit is located between the heat transfer and coolant accommodating surfaces, and traverses the heat transfer surface. The fluid channel defines a flow path for liquid coolant passing through the machine, wherein the flow path extends substantially in a circumferential direction about an axis and progresses in opposite directions parallel to the axis. Also, a method of liquid-cooling a rotary electric machine includes a step of making a liquid coolant flow traverse an approximately cylindrical heat transfer surface along a flow path extending substantially in a circumferential direction about an axis and progressing in opposite directions parallel to the axis between a fluid channel entry and a fluid channel exit.

Description

TECHNICAL FIELD [0001] The present invention relates to a liquid-cooled rotary electric machine having a cooling jacket having a bidirectional flow,

Cross reference of related applications

This application claims priority to each of the following patent applications. Quot; LIQUID-COOLED ROTARY ELECTRIC MACHINE HAVING COOLING JACKET WITH BI-DIRECTIONAL FLOW ", filed Mar. 4, 2013, entitled " LIQUID-COOLED ROTARY ELECTRIC MACHINE WITH BI- 13 / 784,227; Quot; filed March 4, 2013, entitled " LIQUID-COOLED ROTARY ELECTRIC MACHINE HAVING FLUID CHANNEL WITH AUXILIARY COOLANT GROOVE " 13 / 784,390; U.S. Patent Application No. 13 / 784,789, filed Mar. 4, 2013, entitled " LIQUID-COOLED ROTARY ELECTRIC MACHINE HAVING AXIAL END COOLING "; And U.S. Patent Application No. 13 / 075,753, filed March 4, 2013, entitled " LIQUID-COOLED ROTARY ELECTRIC MACHINE HAVING HEAT SOURCE-SURROUNDING FLUID PASSAGE & 784,799.

Technical field

BACKGROUND OF THE INVENTION 1. Field of the Invention The present disclosure relates to a rotary electric machine such as a generator, an alternator, and a motor capable of rotating unidirectionally or bi-directionally about an axis, and more particularly to such a rotary electric machine of liquid-cooled type.

Rotating electrical machines are operated at increasingly higher internal temperatures and the need to improve the cooling of such machines to increase their performance and reliability is increasing. Although air cooled rotary electric machines are common, the specific operating environment of such machines is not suitable for air cooling of rotary electric machines. Such an environment can be achieved, for example, by placing the machine in close proximity to a heated component that has less space around the machine for air circulation or replacement, or that warms the cooling air to the machine, or that ambient air clogs the air passageway of the machine, (E.g., dust, garbage) that can block the airflow passing through it and prevent proper cooling.

It is known to include a rotating electrical machine in a cooling circuit dedicated to machine cooling, or to liquid cool the rotating electrical machine using other components to be cooled. Typically, such circuitry includes a pump for causing a coolant flow through the circuit and a heat exchanger for removing heat from the coolant, which may be, for example, a water, oil or glycol solution. The coolant is provided in a pressurized condition to the coolant inlet of the machine and circulates through the machine to absorb heat by convective heat transfer and is discharged from the machine through the coolant outlet where the inlet and outlet of the machine coolant are located at the point . Such cooling circuits are well known and beyond the scope of the present disclosure and therefore are not further described in detail herein.

Minimizing the size of a rotating electrical machine while maximizing heat removal from the machine is critical to its reliability and successful long-term operation.

According to the present disclosure, there is provided a structure and method for improving liquid cooling of a rotating electrical machine and / or an additional heat source within such a machine.

The present disclosure provides a liquid-cooled rotary electric machine including a stator having a central axis and a rotor surrounded by the stator and rotating about the stator about a central axis. The machine includes a jacket having a stator and an inner volume in which the rotor is disposed, the jacket surrounding the stator and in conductive thermal communication with the stator. The jacket forms a radially outer heat transfer surface with respect to the central axis. The machine includes a fluid channel having an inlet and an outlet, the fluid channel extending between the fluid channel inlet and the outlet and crossing the heat transfer surface of the jacket. The fluid channel defines a flow path for the liquid coolant passing through the machine, the flow path extending substantially circumferentially about the central axis and proceeding in a direction parallel to the central axis between the inlet and the outlet of the fluid channel. The flow path for the liquid coolant passing through the machine proceeds in opposite directions parallel to the central axis when crossing the heat transfer surface.

Another aspect of the present disclosure is that the machine further comprises a sleeve disposed about the jacket and defining a radially inner coolant receiving surface with respect to the central axis and wherein the fluid channel is disposed between the heat transfer surface of the jacket and the receiving surface of the sleeve will be.

Another aspect of the present disclosure is that the flow path extends continuously in a substantially circumferential direction about a central axis.

Another aspect of the present disclosure is that the flow path formed by the fluid channel proceeds in at least one direction parallel to the central axis independently of extending substantially circumferentially about the central axis.

Also, an aspect of the present disclosure is that the flow path formed by the fluid channel proceeds in both directions parallel to the central axis independently of extending substantially circumferentially about the central axis.

Another aspect of the present disclosure is that the fluid channel includes a plurality of substantially annularly extending first fluid channel portions each having opposite ends. Each first fluid channel portion extending substantially circumferentially about a central axis along each first fluid channel portion between respective opposite ends and the plurality of first fluid channel portions being axially distributed along a central axis . The fluid channel also includes a plurality of second fluid channel portions each in fluid communication with an end of the pair of first fluid channel portions, wherein the flow channel extends along each second fluid channel portion in a direction parallel to the central axis.

A further aspect of the present disclosure is that each of the plurality of second fluid channel portions is in fluid communication with axially adjacent ends of the pair of first fluid channel portions.

A further aspect of the present disclosure is that the flow path progresses axially along a common plurality of second fluid channel portions along a central axis parallel to each other.

A further aspect of the present disclosure is that the ends of a pair of first fluid channel portions fluidly connected by the second fluid channel portion are substantially radially aligned about a central axis.

A further aspect of the present disclosure is that each first fluid channel portion extends between an opposing inlet end and an outlet end and each second fluid channel portion is connected to an inlet end and an outlet end of a pair of first fluid channel portions , Wherein the plurality of first fluid channel portions are fluidly connected to one another continuously through the plurality of second fluid channel portions.

Moreover, an aspect of the present disclosure is that the inlet end and the outlet end of a pair of first fluid channel portions fluidly connected by the second fluid channel portion are axially adjacent to each other. It is also contemplated that an aspect of the present disclosure provides a method of forming a plurality of first fluid channel sections, wherein the inlet and outlet ends of the plurality of first fluid channel sections are substantially radially aligned about a central axis, It is alternating in one direction.

A further aspect of the present disclosure is that the fluid channel includes a third fluid channel portion having opposite ends and extending in a direction generally parallel to the central axis. A third fluid channel portion is disposed between opposite ends of each first fluid channel portion and one end of the plurality of first fluid channel portions is fluidly connected to one end of the third fluid channel portion. The other end of the third fluid channel portion is fluidly connected to one of the fluid channel inlet and the fluid channel outlet.

Moreover, an aspect of the present disclosure is that one end of a different one of the plurality of first fluid channel portions is fluidly connected to the other of the fluid channel inlet and the fluid channel outlet.

Moreover, aspects of the present disclosure are that fluid channel inlets and outlets are in fluid communication with each other through a plurality of interconnecting fluid channel portions comprised of first, second, and third fluid channel portions. A plurality of interconnecting fluid channel portions are in fluid communication with each other in succession.

A further aspect of the present disclosure is directed to a fluid channel comprising a third fluid channel portion fluidly connected to one end of one of the plurality of first fluid channel portions and extending along a third fluid channel portion in a direction parallel to the central axis The progression of the flow path is opposite to the progression along the second fluid channel portion.

Moreover, aspects of the present disclosure are that the progression of the flow path is made in a common direction parallel to the central axis along all of the second fluid channel portions.

A further aspect of the present disclosure is that the fluid channel inlets and outlets are all located in the same direction along the central axis from the rotor.

The present disclosure also provides a liquid cooling method for rotating electrical machines. The method includes the step of causing a flow of liquid coolant along a flow path formed by a fluid channel to traverse a generally cylindrical heat transfer surface disposed about an axis, wherein the flow path extends substantially circumferentially about the axis And proceed in opposite directions parallel to the axis between the fluid channel inlet and the fluid channel outlet.

Another aspect of the present disclosure is that according to the method, the extension of the flow path in a substantially circumferential direction about the axis is independent of the flow path in at least one direction parallel to the axis.

BRIEF DESCRIPTION OF THE DRAWINGS The foregoing aspects of the exemplary embodiments will become more apparent and may be better understood by referring to the following description of embodiments taken in conjunction with the accompanying drawings.
1 is a front perspective view of a first embodiment of a rotating electrical machine according to the present disclosure;
2 is a rear perspective view of the rotating electrical machine of the first embodiment;
3 is a front perspective view of the rotating electrical machine of the first embodiment with the housing sleeve removed;
4 is a rear perspective view of the rotating electric machine of the first embodiment with the housing sleeve removed;
5 is a rear perspective view of the rotating electric machine of the first embodiment with the housing sleeve and the rear cover removed;
6 is a top perspective view of a portion of the rotating electric machine of the first embodiment with the housing sleeve and the rear cover removed;
7 is a cross-sectional view of the rotating electric machine of the first embodiment along line 7-7 of Figs. 6 and 9. Fig.
8 is a cross-sectional view of the rotating electrical machine of the first embodiment along line 8-8 of Figs. 6 and 9. Fig.
Figure 9 is a rear end view of the rotating electrical machine of the first embodiment without its rear cover, taken along line 9-9 of Figure 7;
10 is a partial cross-sectional top view of a portion of a rotating electrical machine of a first embodiment showing a flow path for a passing liquid coolant;
11 is a front perspective view of a second embodiment of a rotating electrical machine according to the present disclosure;
12 is a rear perspective view of the rotating electrical machine of the second embodiment;
13 is a front perspective view of the rotating electrical machine of the second embodiment with the housing sleeve removed;
14 is a rear perspective view of the rotating electric machine of the second embodiment with the housing sleeve removed;
15 is a rear perspective view of the rotating electrical machine of the second embodiment with the housing sleeve and the rear cover removed;
16 is a top perspective view of a portion of the rotating electric machine of the second embodiment with the housing sleeve and the rear cover removed;
17 is a cross-sectional view of the rotating electrical machine of the second embodiment along lines 17-17 of Figs. 16 and 19. Fig.
18 is a cross-sectional view of the rotating electrical machine of the second embodiment along lines 18-18 of Figs. 16 and 19. Fig.
Fig. 19 is a rear end view of the rotating electric machine of the second embodiment, taken along line 19-19 of Fig. 17, without its rear cover; Fig.
20 is a partial cross-sectional top view of a portion of a rotating electrical machine of a second embodiment showing a flow path for a passing liquid coolant;
21 is a rear perspective view of the rotating electric machine of the third embodiment according to the present disclosure with the housing sleeve and the rear cover removed;
22 is a top perspective view of a portion of the rotating electric machine of the third embodiment with the housing sleeve and the rear cover removed;
23 is a cross-sectional view of the rotating electrical machine of the third embodiment along the line 23-23 of Fig. 22 and the central axis of the machine;
24 is a cross-sectional view of the rotating electrical machine of the third embodiment along line 24-24 of FIG. 22 and the central axis of the machine;
Figure 25 is a rear end view of the rotating electrical machine of the third embodiment taken along line 25-25 of Figure 23 without the rear cover;
26 is a partial cross-sectional exploded side view of the rotating electric machine of the fourth embodiment according to the present disclosure;
27 is a front perspective view of a fifth embodiment of a rotating electrical machine according to the present disclosure;
28 is a rear perspective view of the rotating electrical machine of the fifth embodiment;
29 is a front perspective view of the rotating electrical machine of the fifth embodiment with the housing sleeve removed;
30 is a rear perspective view of the rotating electrical machine of the fifth embodiment with the housing sleeve removed;
31 is a rear perspective view of the rotating electrical machine of the fifth embodiment with the housing sleeve and the rear cover removed;
32 is a top perspective view of a portion of the rotating electrical machine of the fifth embodiment with the housing sleeve and the rear cover removed;
33 is a cross-sectional view of the rotating electric machine of the fifth embodiment taken along the line 33-33 of FIG. 32 and FIG. 35;
34 is a cross-sectional view of the rotating electric machine of the fifth embodiment taken along line 34-34 of FIG. 32 and FIG. 35;
Figure 35 is a rear end view of the rotating electrical machine of the fifth embodiment taken along line 35-35 of Figure 33 without the rear cover.
36 is a partial cross-sectional top view of a portion of a rotating electrical machine of a fifth embodiment showing a flow path for a passing liquid coolant;
Corresponding reference characters designate corresponding parts throughout the several views. While the drawings illustrate embodiments of the disclosed apparatus and method, the drawings are not necessarily to scale, and certain features may be exaggerated to better illustrate and describe the present disclosure. Moreover, in the accompanying drawings showing the various figures, cross hatching of the various cross sectional elements may be omitted for the sake of clarity. It should be understood that any omission of cross hatching is for illustrative clarity only.

The embodiments of the disclosure are not intended to be exhaustive or to limit the invention to the precise form disclosed in the following detailed description. Rather, the embodiments are chosen and described to enable those skilled in the art to perceive and understand the principles and practice of the disclosure.

It should be understood that the exemplary rotating electrical machine embodiment described herein is a belt-driven alternator, but may alternatively be another type of driven or driven rotary electric machine, such as a dc generator or motor.

1 to 10 show a rotating electrical machine 40 of the first embodiment. The rotating electrical machine 40 has a rotor 42 and a stator 44 with relative rotation therebetween (Figs. 7 and 8). 1 and 2, the rotating electrical machine 40 has a generally cylindrical housing 52 in which a first coolant fitting 54 and a second coolant fitting 56 are provided. As shown, the liquid coolant is received into the housing 52 through a first coolant fitting 54, which is the coolant inlet for the machine 40, and the liquid coolant is introduced into the second coolant fitting (56). Fittings 54 and 56 can be reversed with a natural inversion of the flow direction of the liquid coolant through the machine in relation to the coolant inlet to the machine 40 and its role as coolant outlet from the machine, It is to be understood that the features of the inlet, outlet, inlet, and / or outlet, etc., and the direction of flow of the coolant along the liquid coolant flow path are similarly reversed.

In connection with the illustrated embodiment, once installed and actuated, the inlet fitting 54 is provided with a compressed liquid coolant from a source external to the rotating electrical machine, such as by a clamped or otherwise fixedly connected coolant supply hose (not shown) And the outlet fitting 56 is similarly coupled to a coolant return hose (not shown) for transferring the coolant exiting the machine 40, and the coolant is then cooled. Typically, the machine 40 is part of a well known type of closed loop coolant system that includes a liquid coolant pump and a heat exchanger (not shown).

Fittings 54 and 56 are secured to a circular, flat, removable rear cover 58, which can be formed from a steel tube and form one axial end of the cylindrical housing 52. The rear cover 58 is rigid and may be formed of a steel plate material having an axially inward end of the fitting 54,56 inserted therein and having an aperture that is attached to the cover 58, such as by brazing. The housing 52 also includes a circular, rigid, flat front cover 60 that may be formed from a steel plate material. The front cover 60 is provided with a central hole through which the shaft 62 passes, and the shaft is rotatable about the central axis 64 and rotatably fixed to the rotor 42. The rotor 42 and the shaft 62 may be rotatable in only one direction about the central axis 64, or in both directions. In the illustrated embodiment, a pulley 66 is rotatably secured to the shaft 62 outside the housing 52 to drive the rotor 42 using a belt (not shown). On the inside of the housing 52, the shaft 62 is supported by a front bearing 68 and a rear bearing 69 as shown in Figs.

The machine 40 includes a generally cylindrical jacket 70 that is in thermal conductive communication with the stator 44 and constitutes a portion of the housing 52. The jacket 70 is preferably cast with a highly thermally conductive rigid material, such as aluminum, for example, but may alternatively contain iron, and / or may be stamped or welded. An open-ended cylindrical sleeve 72 is disposed radially around the jacket 70, which sleeve may be made of metal (e.g., steel or aluminum) or a plastic sheet material, for example. The jacket 70 provides a generally cylindrical radially outer heat transfer surface 74 and the tubular sleeve 72 provides a cylindrical radially inner receiving surface 76 for connection. Between the radially outer heat transfer surface 74 and the radially inner receiving surface 76 is disposed a fluid channel 78 that defines a flow path 80 for liquid coolant through the machine 40. In other words, the fluid channel 78 extends axially between the axially opposite ends of the tubular sleeve 72 and radially in the space between the overlapping radially outer surface 74 and the radially inner surface 76 . At least a portion of the flow path (80) for the liquid coolant passing through the machine (40) follows the fluid channel (78).

As shown, the generally cylindrical radially outer heat transfer surface 74 of the jacket 70 has a plurality of elongated walls 82 and a recess 84 defined and interconnected by the wall 82 . The radially outermost surface of the wall 82 contacts the cylindrical smooth radially inner receiving surface 76 of the sleeve 72 which is substantially non-characteristic. Thus, the fluid channel 78 is radially disposed between the sleeve inner receiving surface 76 and the bottom of the recess 84. The flow path 80 follows the interconnected recess 84. As shown, the cross-section of the fluid channel 78 is substantially rectangular and the shape is substantially uniform, but may be otherwise shaped and / or non-uniform. The hydraulic diameter of the fluid channel 78 may vary along the flow path 80 to affect the desired coolant flow and / or heat transfer state.

The jacket 70 and the sleeve 72 may be formed in a known manner such as by cooling the jacket 70 prior to their assembly and heating the sleeve 72 and then positioning them relative to each other, So that they are attached by interference fit or heat fitting. Alternatively, the jacket and sleeve may be attached by crimping or welding, or by using fasteners (not shown), or by other conventional means. Moreover, it will be appreciated by those skilled in the art that instead of the jacket 70 and sleeve 72 configured as shown, the radially outer heat transfer surface 74 of the jacket is substantially free of features and the radially inner side of the sleeve It will be appreciated that recesses and walls may be provided that form the fluid channel 78 in the receiving surface 76. 7 and 8, a seal 98 is provided between the jacket 70 and the sleeve 72, axially outwardly of the fluid channel 78 and adjacent the axially opposite ends of the sleeve 72 To prevent leakage of coolant from the machine (40).

At the opposite ends of the fluid channel 78, at points along the flow path 80 near the rear axial end of the jacket 70, There are fluid channel inlets 86 and outlets 88 that extend radially inward. The designation of such inlet 86 and outlet 88 may be reversed in accordance with the selected coolant flow direction along flow path 80 through machine 40. [ In the machine 40, the fluid channel 78 includes a plurality of substantially annular first fluid channel portions 90, each extending circumferentially about a central axis 64. The first fluid channel portion 90 is parallel to and parallel to an imaginary plane (not shown) perpendicular to the central axis 64. The fluid channel 78 also includes a plurality of second fluid channel portions 92 each extending between the axially adjacent ends 94 of the pair of first fluid channel portions 90. Each second fluid channel portion 92 includes a pair of successively adjacent first fluid channel portions 90 that extend through the second fluid channel portion 92 to the outlet end 94 of the other first fluid channel portion 90, To the inlet end (94) of a first fluid channel portion (90) fluidly connected to the first fluid channel portion (90). The fluid channel portions 90, 92 provide a series of switchbacks prior to the coolant flow path 80. The fluid channel 78 extends circumferentially about the central axis 64 through the first fluid channel portion 90 and extends through the second fluid channel portion 92 in the direction along the central axis 64 In the axial direction. In the machine 40 a flow path 80 formed by the fluid channel 78 extends substantially circumferentially about the central axis 64 (via the first fluid channel portion 90) (Via the second fluid channel portion 92) in a direction along the central axis 64, independent of the flow path 180 that is in fluid communication with the fluid channel 180.

The fluid channel 78 also includes a generally elongated, generally linear, third fluid channel portion 96 extending in a direction along the central axis 64. As shown, one of the two opposite ends of the fluid channel portion 96 is fluidly connected to the fluid channel inlet 86 and the other is closest to the front cover 60 and closest to the fluid channel inlet 86 Is fluidly connected to the end 94 of the first fluid channel portion 90 that is disposed apart. As described above, the plurality of first fluid channel portions 90 are continuously fluidly connected through the plurality of second fluid channel portions 92 to form a flow path 80. As shown, the fluid channel outlet 88 is disposed at the outlet end 94 of the annular first fluid channel portion 90 disposed closest to the rear cover 58. Thus, fluid channel inlet 86 and outlet 88 are in fluid communication with each other within machine 40 through fluid channel portions 90, 92, and 96 that are connected in series. In a particular, not shown embodiment, the width of the fluid channel 78 formed by any of the fluid channel portions 90, 92 and / or 96 provides a parallel sub-channel along the flow path, And may be partially or wholly divided along the fluid channel length.

The generally cylindrical jacket 70 has an internal volume and an axial end 100 at the rear of the machine 40. The axial end 100 of the jacket partly seals one axial end of the inner volume of the jacket in which the rotor 42 and the stator 44 are located. The fluid chamber 102 is formed by the wall 104 of the axial end 100 of the jacket and is fluidly connected to the fluid channel 78. As shown, fluid chamber 102 is connected to fluid channel 78 through fluid channel inlet 86. In an alternative, non-illustrated embodiment, fluid chamber 102 may be connected to fluid channel 78 through fluid channel outlet 88.

The wall 104 and the rear cover 58 form a substantially annular fluid passage 106 extending between the fluid chamber 102 and the first and second openings 108 and 110 of the fluid passage 106 . The fluid passage 106 also forms a flow passage 80. As shown, the first opening 108 is disposed at the axially inward end of the first coolant fitting 54, which is the coolant inlet for the machine 40, as described above. Alternatively, the first opening 108 of the fluid chamber 102 may be disposed on the cylindrical outer wall of the jacket 70 and the first coolant fitting 54 may be disposed on the cover 58, as described above and shown in the figures, Lt; RTI ID = 0.0 > openings < / RTI > In such an alternative, non-illustrated embodiment, the coolant inlet fitting extends radially from the machine 40 rather than being supported by the cover 58 and extending axially from the cover. The liquid coolant contained within the fluid chamber 102 through the first fitting 54 and the first opening 108 is passed annularly about the central axis 64 along the flow path 80 through the fluid passageway 106, And is directed toward the opening 110. In the illustrated embodiment, the second opening 110 is fluidly connected to the inlet 86 of the fluid distribution chamber 78.

The axial end 100 of the jacket is also provided with a port 112 that is fluidly connected to the outlet 88 of the fluid channel 78 as best seen in FIG. The port 112 is fluidly isolated from the fluid chamber by a gasket or seal 114 that prevents the liquid coolant from leaking radially outward or radially inwardly from the fluid passageway 106 The joint between the jacket 70 and the rear cover 58 is sealed.

A cavity 116 is formed which is defined by the axial end wall 104 of the jacket toward the radially inward side of the annular fluid chamber 102. [ The cavity 116 is substantially surrounded by the seal 114 and the fluid chamber 102. Cavity 116 and fluid chamber 102 are in an electrothermal communication relationship through wall 104 separating them. A heat source 118 in the form of a power electronics module 120 is disposed in the cavity 116 and in conductive thermal communication with the wall 104. The power electronics module 120 is of a suitable configuration and may be configured to control power to induce relative rotation between the rotor 42 and the stator 44 or to control the power generated by their relative rotation, And are of a type known in the art. The shaft rear bearing 69 supported in the bearing mount 122 formed by the wall 104 of the axial end 100 of the jacket is another heat source 118 of the machine 40.

The heat transferable from the heat source (s) 118 through the jacket's axial end wall (s) 104 may be convectively transferred to the liquid coolant along the flow path (80) in the fluid path (106). Heat from the stator 44 and the additional heat source (s) 118 (e.g., power electronics module 120 and / or rear bearing 69) is transmitted through the cylindrical wall of the jacket 70 and the axial direction of the jacket Can be convectively conveyed to the liquid coolant along the flow path (80) through the end (100).

The flow path 80 for the liquid coolant passing through the machine 40 begins at the first coolant fitting 54 and flows through the annular fluid passageway 106 and through the fluid channel 78 Lt; RTI ID = 0.0 > 56 < / RTI > More specifically, the liquid coolant received in the machine 40 through the coolant inlet 54 is received into the fluid chamber 102 through the first opening 108 and flows through the second opening 110 through the fluid passageway 106, And enters the inlet 86 of the fluid distribution channel 78 through the second opening 110 and continues in the direction along the central axis 64 through the third fluid channel portion 96 to the forward Toward the connected inlet end 94 of the first fluid channel portion 90 which is disposed closest to the cover 60. [ The liquid coolant in the first fluid channel portion 90 is guided in the jacket recess 84 defined by the jacket wall 82 between the interfaces 74 and 76 of the jacket 70 and the sleeve 72, 64 in the circumferential direction. When the liquid coolant reaches the opposite outlet end 94 of the first fluid channel portion 90 the liquid coolant continues axially through the second fluid channel portion 92 generally in a direction along the central axis 64 Toward the inlet end 94 of the first fluid channel portion 90 that is oriented and axially adjacent and toward the opposite outlet end 90 of the first fluid channel portion 90 adjacent thereto along the first fluid channel portion And flows in the circumferential direction about the central axis 64. [ The flow path 80 of the liquid coolant continues in this manner through the first and second continuously connected portions 90, 92 of the fluid channel 78 until it reaches the outlet 88 of the fluid channel 78 do. The coolant flows out of the fluid channel 78 through the outlet 88 and toward the port 112 and out of the port 40 through the second coolant fitting 56 from the port. 9 and 10, the illustrated flow path 80 for the liquid coolant passing through the machine 40 is indicated by the directional arrow. Alternatively, the port 112 may be disposed on the cylindrical outer wall of the jacket 70 and the second coolant fitting 56 may be secured to the outer wall of the cover 58 rather than being fixed to the cover 58 as described above and shown in the drawings Loses. In such an alternative, non-illustrated embodiment, the coolant outlet fitting extends radially from the machine 40 rather than being supported by the cover 58 and extending axially from the cover.

11-20 illustrate a rotating electrical machine 140 of a second embodiment that is substantially identical in structure, operation and function to the rotating electrical machine 40 of the first embodiment, as shown in the drawings and described herein, have. Features that are peculiar to the machine 140 of the second embodiment and that can be significantly different from the respective corresponding features of the machine 40 of the first embodiment are the same as those associated with each feature of the machine 40 of the first embodiment Indicated by the reference numeral denoted by the sum of 100 plus the reference number.

The machine 140 of the second embodiment includes a generally cylindrical housing 152 having a first coolant fitting 154 and a second coolant fitting 56. [ As shown, the liquid coolant is received into the housing 152 through a first coolant fitting 154, which is the coolant inlet for the machine 140, and the liquid coolant is delivered to the second coolant fitting (56). The fittings 154 and 56 may be provided with respect to the coolant inlet or coolant outlet of the machine 140 along with the natural reversal of the direction of flow of the liquid coolant through the machine, as described above in connection with the machine 40 of the first embodiment. Can be reversed. The features of the inlet, outlet, inlet, and / or outlet, etc., relative to the flow direction of the coolant along the liquid coolant flow path are likewise reversed. The machine 140 of the second embodiment can be replaced by a liquid cooling circuit for the machine 40 of the first embodiment in which the compressed liquid coolant from the source outside the rotating electrical machine 140 is similarly And the outlet fitting 56 is similarly connected to a coolant return hose (not shown).

The fitting 154 itself is structurally identical to the fitting 54 and is connected to the removable rear cover 158 in a manner similar to the connection of the fitting 54 to the rear cover 58. The rear cover 158 itself is structurally similar to the rear cover 58 and the main difference between them is the position of each of the fittings 54,154. As best seen in Figures 12 and 14, the coolant fittings 154 are centered substantially coaxially with the central axis 64 in the circular cover 158.

The machine 140 includes a generally cylindrical jacket 170 that is in thermal conductive communication with the stator 44 and constitutes a portion of the housing 152. The relationship of the material of the jacket 170 and the jacket to the stator 44 is substantially the same as described above with respect to the jacket 70 of the machine 40 of the first embodiment. Moreover, the jacket 170 and the cylindrical sleeve 72 cooperate to form a fluid channel 78 as described above with respect to the machine 40. The fluid channel (78) forms a flow path (180) for the liquid coolant passing through the machine (140).

15 to 19, a generally cylindrical jacket 170 has an inner volume and an axial end 200 at the rear of the machine 140 surrounding the axial end of the inner volume of the jacket, The rotor 42 and the stator 44 are disposed. The fluid chamber 202 is formed by the wall 204 of the jacket axial end 200 and the fluid chamber 202 is fluidly connected to the fluid channel 78 described above through the inlet 86. The wall 204 and cover 158 of the axial end 200 of the jacket form a generally helical fluid passage 206 extending between the first opening 208 and the second opening 210. The first opening 208 is disposed at the axially inward end of the first coolant fitting 154 which is the coolant inlet to the machine 140. The liquid coolant received through the first coolant fitting 154 into the fluid chamber 202 flows through the runner 206 along the flow path 180 toward the second opening 210 outwardly about the central axis 64 . The second opening 210 is fluidly connected to the inlet 86 of the fluid distribution channel 78. A port 112 is provided at the axial end 200 of the jacket to fluidly connect to the outlet 88 of the fluid channel 78, such as the jacket axial end of the machine 40. The port 112 is fluidly isolated from the fluid chamber 202 by a gasket or seal 214 and the gasket or seal also includes a jacket 170 and a removable rear cover 202 to prevent leakage of liquid coolant from the fluid chamber 202. [ (158).

The axial end 200 of the jacket is provided with a generally flat axial inner surface 216 formed by the axial end wall 204 of the jacket. The inner surface 216 and the fluid chamber 202 are in conductive thermal communication therewith through these separating walls 204. A first heat source 218 in the form of a power electronics module 220 is disposed with respect to the inner surface 216 and in conductive thermal communication with the wall 204. The power electronics module 220 is suitably configured to control the power that induces relative rotation between the rotor 42 and the stator 44 or to control the power generated by their relative rotation, And are of a type known in the art. The shaft rear bearing 69 supported in the bearing mount 222 formed by the wall 204 of the jacket axial end 200 is another heat source 218 of the machine 40.

The heat transferable from the heat source (s) 218 through the jacket's axial end wall (s) 204 may be convectively transferred to the liquid coolant along the flow path 180 in the fluid path 206. Heat from the stator 44 and the additional heat source (s) 218 (e.g., power electronics module 220 and / or rear bearing 69) is applied to the cylindrical wall of the jacket 170 and the axial direction of the jacket May be convectively conveyed to the liquid coolant along the flow path 180 through the end 200.

The flow path 180 for the liquid coolant flowing through the machine 140 begins at the first coolant fitting 154 and flows along the helical fluid path 206 and through the fluid channel 78 Lt; RTI ID = 0.0 > 56 < / RTI > More specifically, as in the machine 40 of the first embodiment, the liquid coolant contained in the machine 140 through the coolant inlet 154 is received into the fluid chamber 202 through the first opening 208, Flows outwardly about the central axis 64 through the passageway 206 and enters the inlet 86 of the fluid distribution channel 78 through the second opening 210 and enters the third fluid channel portion 96 To the connected inlet end 94 of the first fluid channel portion 90 which continues in the direction along the central axis 64 and closest to the front cover 60. [ The liquid coolant in the first fluid channel portion 90 is transferred between the interface 74 and 76 of the jacket 170 and the sleeve 72 within the jacket recess 84 defined by the jacket wall 82, 64 in the circumferential direction. As described above, when the liquid coolant reaches the opposite outlet end 94 of the first fluid channel portion 90, as in the machine 40 of the first embodiment, the liquid coolant flows into the second fluid channel portion 92 ) Toward the inlet end (94) of the axially adjacent first fluid channel portion (90) in a direction that is generally axially oriented in a direction generally along the central axis (64) 1 fluid channel portion 90 toward the opposite outlet end 90 of the first fluid channel portion 90. [ The liquid coolant flow path 180 continues in this manner through the first and second continuously connected portions 90 and 92 of the fluid channel 78 until it reaches the outlet 88 of the fluid channel 78 do. The coolant flows out of the fluid channel 78 through the outlet 88 and toward the port 112 and out of the port 40 through the second coolant fitting 56 from the port. 19 and 20, the illustrated flow path 180 for the liquid coolant passing through the machine 140 is indicated by the directional arrow. Alternatively, the first opening 208 of the fluid chamber 202 may be disposed on the cylindrical outer wall of the jacket 170 and the first coolant fitting 154 may be disposed on the cover 158, as described above and shown in the figures, Rather than being fixed to the outer wall. Alternatively, the port 112 may be disposed on the cylindrical outer wall of the jacket 170 and the second coolant fitting 56 may be disposed on the outer wall of the jacket 170 rather than being fixed to the cover 158, Respectively. In such an alternative, non-illustrated embodiment, the coolant inlet and outlet fittings extend radially from the machine 40 rather than being supported by the cover 158 and extending axially from the cover.

Figures 21 to 25 illustrate a rotating electrical machine 240 of a third embodiment that is substantially identical in construction, operation and function to the rotating electrical machine 40 of the first embodiment shown in the drawings and described herein, have. Features that are peculiar to the machine 240 of the third embodiment and that can be significantly different from the respective corresponding features of the machine 40 of the first embodiment are those associated with each feature of the machine 40 of the first embodiment Indicated by the reference numeral denoted by the sum of 200 plus the reference number. The appearance of the machine 240 is similar to the appearance of the machines 40 and 140 but is similar to the appearance of the first coolant fittings 54 and 154 and the rear covers 58 and 158 of the machines 40 and 140, For the placement of coolant inlet fittings 254 to the rear cover 258 as far as possible. The generally cylindrical housing 252 of the machine 240 of the third embodiment also includes a coolant outlet 56. The first coolant fitting 254 and the second coolant fitting 56 of the machine 240 of the third embodiment are connected to the machine 240 as described above with respect to the machines 40 and 140 of the first and second embodiments. May be fluidly connected to the remainder of the liquid cooling circuit and reversed with a natural reversal of the flow direction of the liquid coolant through the machine. The features of the inlet, outlet, inlet, and / or outlet, etc., relative to the flow direction of the coolant along the liquid coolant flow path are likewise reversed.

The generally cylindrical jacket 270 of the machine 240 constitutes a part of the housing 252 and is similar to the jacket 70 of the machine 40 of the first embodiment. The jacket 270 is in thermal conductive communication with the stator 44 and cooperates with the cylindrical sleeve 72 to form a fluid channel 78 therebetween as described above with respect to the machine 40, The fluid channel (78) forms a flow path (280) for the liquid coolant passing through the machine (240).

A generally cylindrical jacket 270 has an inner volume and an axial end 300 rearward of the machine 240 that partially surrounds the axial end of the inner volume of the jacket, A stator 44 is disposed. The fluid chamber 302 is formed by the wall 304 of the jacket axial end 300 and the fluid chamber 302 is fluidly connected to the fluid channel 78 described above through the inlet 86. The wall 304 and the removable rear cover 258 form a generally S-shaped fluid passage 306 extending between the first opening 308 and the second opening 310. The first opening 308 is disposed at the axially inward end of the first coolant fitting 254 which is the coolant inlet for the machine 240. The liquid coolant received through the first coolant fitting 254 into the fluid chamber 302 is directed through the fluid passage 306 toward the second opening 310 along the serpentine flow path 280. The second opening 310 is fluidly connected to the inlet 86 of the fluid distribution channel 78. A port 112 is provided at the axial end 300 of the jacket such that the jacket axial end 100 of the machine 40 is fluidly connected to the outlet 88 of the fluid channel 78. The port 112 is fluidly isolated from the fluid chamber 302 by a gasket or seal 314 and the gasket or seal also includes a jacket 270 and a removable rear cover 302 to prevent leakage of liquid coolant from the fluid chamber 302. [ (258).

A first cavity 316 and a second cavity 317 are defined by a wall 304 at the axial end 300 of the jacket and each cavity extends between the cavities 316 and 317 to separate the cavities from each other And is substantially surrounded by a portion of the S-shaped fluid chamber 302. Each of the cavities 316, 317 and the chamber 302 are in conductive heat communication through a wall 304 separating them. A heat source 318 in the form of a first power electronics module 320 is disposed within the first cavity 316 and in conductive thermal communication with the cavity forming wall 304. Another heat source 318 in the form of a second power electronics module 321 is disposed in the second cavity 317 and in conductive thermal communication with the cavity forming wall 304. Each power electronics module 320,321 is suitably configured and configured to control power to induce relative rotation between the rotor 42 and the stator 44 or to control the power generated by their relative rotation Lt; RTI ID = 0.0 > known < / RTI > in the art. The S-shaped pattern of fluid passageways 306 allows module 320, 321 to have liquid coolant passageways on its three sides, allowing maximum coolant contact with wall 304 for a given heat source package size, Lt; / RTI > Moreover, the shaft rear bearing 69, which is supported in a bearing mounting portion 322 defined by the wall 304 of the axial end 300 of the jacket, can also act as a heat source 318 during operation of the machine 240 .

The heat transferable from the heat source (s) 318 through the jacket axial end wall 304 may be convectively transferred to the liquid coolant along the flow path 280 in the fluid path 306. Heat from the stator 44 and the additional heat source 318 (e.g., power electronics modules 320, 321 and / or rear bearings 69) is applied to the cylindrical wall of the jacket 270 and the axial ends of the jacket May be convectively conveyed to the liquid coolant along flow path 280 through conduit 300.

The flow path 280 for the liquid coolant flowing through the machine 240 begins at the first coolant fitting 254 and flows along the S-shaped fluid path 306 and through the fluid channel 78. [ Lt; RTI ID = 0.0 > 56 < / RTI > More specifically, the liquid coolant contained in the machine 240 through the coolant inlet 254 is received into the fluid chamber 302 through the first opening 308 and extends circumferentially about the respective cavity 316, 317 And flows along the substantially enclosing tubular fluid passageway 306 and enters the inlet 86 of the fluid channel 78 through the second opening 310. In the fluid channel 78, as in the machines 40 and 140 of the first and second embodiments, the coolant continues in the direction along the central axis 64 through the third fluid channel portion 96, (94) of the first fluid channel portion (90) that is disposed closest to the first fluid channel portion (60). The liquid coolant in the first fluid channel portion 90 extends between the interface 74 and 76 of the jacket 270 and the sleeve 72 within the jacket recess 84 defined by the jacket wall 82, 64 in the circumferential direction. As the liquid coolant reaches the opposite outlet end 94 of the first fluid channel portion 90, as in the machines 40, 140 of the first and second embodiments, the liquid coolant flows into the second fluid channel portion 92 ) Toward the inlet end (94) of the axially adjacent first fluid channel portion (90) in a direction that is generally axially oriented in a direction generally along the central axis (64) 1 fluid channel portion 90 toward the opposite outlet end 90 of the first fluid channel portion 90. [ The liquid coolant flow path 280 continues in this manner through the first and second continuously connected portions 90 and 92 of the fluid channel 78 and through the outlet 88 of the fluid channel 78 to the port & And flows out of the machine 240 through the second coolant fitting 56 toward the second coolant outlet 112. [ Referring to Fig. 25, the illustrated flow path 280 for the liquid coolant passing through the machine 240 is indicated by the directional arrow. Alternatively, the first opening 308 of the fluid chamber 302 may be disposed on the cylindrical outer wall of the jacket 270 and the first coolant fitting 254 may be disposed on the cover 258, as described above and shown in the figures. Rather than being fixed to the outer wall. Alternatively, the port 112 may be disposed on the cylindrical outer wall of the jacket 170 and the second coolant fitting 56 may be disposed on the outer wall of the jacket 170, rather than being secured to the cover 258, Respectively. In such alternative non-illustrated embodiment (s), the coolant inlet and outlet fittings are supported by the cover 258 and extend radially from the machine 240 rather than extending axially from the cover.

26 is similar to the machine 240 of the third embodiment and includes a rotating electrical machine 340 of a fourth embodiment including an alternative non-illustrated variant in which coolant inlet and outlet fittings extend radially from the cylindrical wall of the jacket, FIG. However, in the machine 340, the first and second power electronics modules 420 and 421, which are similar to the power electronics modules 320 and 321 of the machine 240 of the second embodiment, are provided with a removable rear cover 358, Is a heat source (418) mounted on the heat exchanger. The rear cover 358 of the machine 340, its components of the housing 352, is otherwise similar to the rear cover 258 of the machine 240. As in the machine 240 of the third embodiment, the power electronics 420 and 421 are received in cavities 316 and 317 of the jacket 270 and these heat sources 418 are located at the axial end 300 of the jacket, Is in conductive heat communication with the wall (304) The rear bearing 69 is another heat source 418 of the machine 340. From the point of view of the machine 340 of the fourth embodiment, an embodiment (not shown) of a rotating electrical machine having a heat source similar to the other machines disclosed herein, but mounted on its rear cover, is readily conceivable.

Figures 27 to 36 illustrate a rotating electrical machine 440 of the fifth embodiment. The machine 440 includes a rotor 42 and a stator 444 (Figures 33 and 34) with relative rotation therebetween. 27 and 28, the machine 440 has a generally cylindrical housing 452 in which a first coolant fitting 454 and a second coolant fitting 456 are provided. As shown, the liquid coolant is received into the housing 452 through a first coolant fitting 454, which is the coolant inlet for the machine 440, and the liquid coolant is introduced into the second coolant fitting 452, which is the coolant outlet from the machine 440, And is discharged from the housing 452 through the opening 456. Fittings 454 and 456, as in the previous embodiments, are associated with a coolant inlet to the machine 40 and their role as coolant outlets from the machine, along with a natural reversal of the flow direction of the liquid coolant through the machine, And features such as inlet, outlet, inlet, and / or outlet for the flow direction of the coolant along the liquid coolant flow path are likewise reversed.

Typically, as in the previous embodiments, the machine 440 is part of a well known type of closed loop coolant system that includes a liquid pump and a heat exchanger (not shown). In connection with the illustrated embodiment, once installed and actuated, the inlet fitting 454 is provided with a compressed liquid coolant from a source external to the rotating electrical machine, such as by a clamped or otherwise fixedly connected coolant supply hose (not shown) do. The outlet fitting 56 is similarly coupled to a coolant return hose (not shown) that transfers the coolant exiting the machine 440, and the coolant is then cooled.

The fittings 454 and 456 can be formed of steel tubes and are fixed to a circular flat front cover 460 and a rear cover 458, respectively, which form opposite front and rear axial ends of the cylindrical housing 452. The covers 458 and 460 are rigid and the axially inward ends of the fittings 454 and 456 may be inserted and formed of a steel plate material having apertures to be attached, such as by brazing. The front cover 460 is also provided with a central hole through which the shaft 62 is passed and the shaft is rotatable about the central axis 64 and rotatably secured to the rotor 42. The pulley 66 is rotatably fixed to the shaft 62 on the outside of the housing 452. In the interior of the housing 452, the shaft 62 is supported by a front bearing 68 and a rear bearing 69 as shown in Figs. 33 and 34.

The machine 440 includes a generally cylindrical jacket 470 that is in thermal conductive communication with the stator 444 and constitutes a portion of the housing 452. The jacket 470 is preferably cast with a highly thermally conductive rigid material, such as aluminum, for example, but may alternatively contain iron and / or may be stamped or welded. A tubular sleeve 472 is disposed radially about the jacket 70, and the sleeve can be made of, for example, a metal or plastic sheet material. The jacket 470 provides a generally cylindrical radially outer heat transfer surface 474 and the tubular sleeve 472 provides a cylindrical radially inner receiving surface 476 for connection. Between the radially outer heat transfer surface 474 and the radially inner receiving surface 476 is disposed a fluid channel 478 defining a flow path 480 for the liquid coolant passing through the machine 440. In other words, the fluid channel 478 is disposed radially between the opposite ends of the tubular sleeve 472 in the axial direction and within the space between the overlapped outer surface 474 and the inner surface 476. At least a portion of the flow path 480 for the liquid coolant passing through the machine 440 follows the fluid channel 478.

The jacket 470 and the sleeve 472 may be formed by known methods such as by cooling the jacket 470 prior to their assembly and heating the sleeve 472, And can be forced or thermally fit together. Moreover, it will be appreciated by those skilled in the art that instead of being constructed as shown, the radially outer heat transfer surface 474 of the jacket may be substantially featureless, and that the radially inner receiving surface 476 of the sleeve may have a fluid channel It will be appreciated that features for forming are provided. 33 and 34, a seal 498 is provided between the jacket 470 and the sleeve 472 at the opposite axial end.

A generally cylindrical radially outer heat transfer surface 474 of the jacket 470 extends circumferentially about the central axis 64 at a uniform pitch and axially in a direction along the axis to form a fluid channel 478 A continuous spiral groove 482 is provided. As shown, the cross-section of the helical groove 482 may be substantially rectangular and the shape may be substantially uniform, but may vary along the flow path 480 to affect the coolant flow and / or the desired heat transfer state. The portion of the radially outer heat transfer surface 474 outside of the helical groove 482 contacts the cylindrical smooth radially inner receiving surface 476 of the sleeve 472 substantially free of features. Thus, a portion of the fluid channel 478 is radially disposed between the inner receiving surface 476 of the sleeve and the bottom of the groove 482.

In machine 440 the helical groove 482 forms a primary or first portion of the fluid channel 478 that extends circumferentially about the central axis 64 and proceeds in a direction along the central axis 64 . Simultaneous circumferential extension and axial advancement of the fluid channels 478 formed by the helical grooves 482 around the central axis 64 and along the central axis are interdependent. In other words, the flow path 480 formed by the fluid channel 478 proceeds in a direction along the central axis 64 in accordance with the flow path 480 extending in a substantially circumferential direction about the central axis 64 .

At the opposite ends 484 and 485 of the helical groove 482 there are an inlet 486 and an outlet 488 of the fluid channel 478 at points along the flow path 480, respectively. The inlet 486 and the outlet 488 extend through the jacket 470 toward the radially inward side of the sealing engagement between the jacket 470 and the sleeve 472, respectively. The designation of such inlet 486 and outlet 488 may be reversed along the selected coolant flow direction along flow path 480 through machine 440. [ Fittings 454 and 456 are disposed at opposite ends of the helical groove 482 and are secured within the holes provided in the cylindrical sleeve 472 and the fluid channel inlets 486 and a fluid channel outlet 488, respectively. In such an alternative embodiment, the fittings 454 and 456 may be configured to extend radially from the machine 440 rather than being supported by the covers 460 and 458 and extending axially from the cover, do.

A conventional liquid-liquid rotary electric machine is known which includes a generally cylindrical heat transfer surface, similar to groove 482, having a helical groove forming a spiral fluid channel. Depending on the size and pitch of the grooves forming such helical fluid channels, the zones of the heat transfer surfaces of these conventional machines are such that, for the remainder of the heat transfer surface, these zones are not crossed by the fluid channels, May be present where minimal cooling activity occurs. Such zones may be places where the heat is locally excessive.

The fluid channel 478 of the machine 440 also includes a pair of auxiliary coolant grooves 490 and 491 on the heat transfer surface 474 to handle this disadvantage of the conventional liquid cooled rotary electric machine. The secondary coolant grooves 490 and 491 form a secondary portion of the fluid channel 478 and a liquid coolant flow path 480 through the machine 440. As shown, each of the supplemental coolant grooves 490, 491 is substantially semicircular in shape and has a substantially uniform size along its length, and these features are provided by a coolant flow along these features and from the associated area or area Lt; RTI ID = 0.0 > heat transfer. ≪ / RTI > The cross-sectional size of the secondary fluid channel portion formed by the secondary coolant grooves 490, 491 is substantially smaller than the cross-sectional size of the primary fluid channel portion formed by the helical grooves 482. Thus, the flow rate of the liquid coolant through the auxiliary coolant grooves 490, 491 is substantially less than the flow rate of the liquid coolant through the helical grooves 482.

For the coolant flow direction along the flow path 480 the first encountering auxiliary coolant groove 490 extends between the first point 492 and the second point 493 which are spaced along the helical groove 482 . In the illustrated embodiment, the first point 492 and the second point 493 are circumferentially spaced approximately 360 ° around the central axis 64. Thus, the first point 492 and the second point 493 may be aligned substantially radially about the central axis 64 as shown. The points 492 and 493 are also axially spaced apart by a substantially uniform pitch length of the helical groove 482. The first point 492 is disposed near the end 484 of the helical groove 482 adjacent the fluid channel inlet 486. The second point 493 is disposed axially inward of the first point 492, i.e. away from the inlet 486 and in a direction along the central axis 64 towards the outlet 488. Thus, near its end 484, the helical groove 482 is fluidly connected to its axially inward portion through the auxiliary coolant groove 490. [ The location of the second point 493 facing axially inward is such that the helical groove 482 extends from the heat transfer surface 474 in the direction of coolant flow along the helical groove 482 to a first circumferential It is near the point to complete the direction extension. Thus, at the first point 492, the spiral groove / fluid channel primary portion 482 is fluidly connected to itself at the second point 493 through the fluid channel secondary portion 490. [

Similarly, a second encountering auxiliary coolant groove 491 extends between the third point 494 and the fourth point 495, which are spaced along the helical groove 482. In the illustrated embodiment, the third and fourth points 494, 495 are circumferentially spaced approximately 360 degrees about the central axis 64. [ Thus, the third point 494 and the fourth point 495 can be aligned substantially radially about the central axis 64 as shown. The points 494 and 495 are also axially spaced by a substantially uniform pitch length of the helical groove 482. A fourth point 492 is disposed adjacent to the end 485 of the helical groove 482 adjacent the fluid channel outlet 488. The third point 494 is disposed axially inward of the fourth point 495, i.e., away from the outlet 488 and in a direction along the central axis 64 towards the inlet 486. Thus, near its end 485, the helical groove 482 is fluidly connected to its axially inward portion through the supplementary coolant groove 491. The location of the axially inwardly facing third point 494 is such that the helical groove 482 extends in the direction of coolant flow along the helical groove 482 in the final circumferential direction about the central axis 64 at the heat transfer surface 474 It is near the point where the extension begins. Thus, at the third point 494, the spiral groove / fluid channel primary portion 482 is fluidly connected to itself at the fourth point 495 through the fluid channel secondary portion 491. [

Each secondary coolant groove / fluid channel secondary portion 490, 491 extends between each pair of points 492, 493 or 494, 495 and a larger size helical groove 482 extends beyond the heat transfer surface 474 (496, 497). ≪ / RTI > Unless otherwise provided for the provision of the auxiliary coolant grooves 490 and 491, the regions 496 and 497 may otherwise be improperly cooled and become undesirable excessive heat locations. The areas 496 and 497 are roughly represented by the shading areas of Figs. 29 to 32 and Fig. As best seen in FIG. 36, the shapes of the two complementary coolant grooves 490, 491 may be substantially mirror images of one another, and otherwise substantially the same. As shown, each supplemental coolant groove 490, 491 is curved and extends well into its respective region 496, 497.

Referring to the left side of FIG. 36, the liquid coolant is held in a pressurized state into the inlet 486 of the fluid channel 478. A small portion of the liquid coolant flowing into the fluid channel 478 is directed to the first coinciding supplementary coolant groove 490 at the first point 492 and a portion of the liquid coolant flowing into the fluid channel 478 through the fluid channel 478, A large portion of the liquid coolant flow continues along the helical groove 482. A small portion of the liquid coolant received within the auxiliary coolant groove 490 is conveyed along the groove through the first encountering region 496 in the space between the superimposed surfaces 474 and 476 and at a second point 493, Convectively absorbs heat from the region 496 before recombining with a large portion of the branched liquid coolant flow through the groove 482 and the coolant flow through the fluid channel 478 on the downstream side of the second point is no longer Until it encounters the third point 494 without branching. The liquid coolant initially received into the auxiliary coolant grooves 490 at the first point 492 flows into the region 496 and into the vertex 464 formed by the grooves 490 in a direction generally opposite to the flow through the helical groove 482. [ (499). Along the groove 490, a vertex 499 is disposed between points 492 and 493. When the coolant flowing through the groove 490 reaches its apex 499, the general coolant flow direction along the groove 490 changes in the coolant flow direction through the generally helical groove 482. The flows of liquid coolant through the grooves 490, 482 then converge and are merged at the second point 493. Specifically, at the first point 492, an opening toward the auxiliary coolant groove 490 is oriented relative to the helical groove 482 to receive the liquid coolant in the pressurized state. At the second point 493 an opening from the auxiliary coolant groove 490 is oriented relative to the helical groove 482 to facilitate the merging of a small portion and a large portion of the liquid coolant flow along the flow path 480 .

Referring to the right side of Fig. 36, the liquid coolant is conveyed in a pressurized state through the helical groove 482 on the downstream side of the second point 493. A small portion of the liquid coolant flow through the fluid channel 478 is received within the opening of the second coinciding coolant groove 491 at the third point 494 and a small portion of the branched liquid coolant flow passes through the third point 494 through the inlet opening toward the auxiliary coolant groove 491 and along the helical groove 482 toward the fluid channel outlet 488. Near the outlet 488, the auxiliary coolant groove 491 is fluidly connected to the helical groove 482 of the fourth point 495, and at the fourth point, a small portion of the branched liquid coolant flow through the auxiliary coolant groove 491 The portion is reintroduced into the larger portion. The integrated liquid coolant then exits the fluid channel 478 through the outlet 488. A small portion of the liquid coolant received into the auxiliary coolant groove 491 is conveyed along the groove through the first encountering region 496 in the space between the superimposed surfaces 474 and 476 and at the fourth point 495, Convectively absorbs heat from the region 497 prior to recombining with a large portion of the liquid coolant flow branched through the groove 482 and the coolant flow through the fluid channel 478 on the downstream side of the fourth point is no longer Integrated without branching. The liquid coolant initially received into the auxiliary coolant groove 491 at the third point 494 is discharged into the region 497 and into the groove 490 in a direction substantially the same as the direction of the coolant flow through the helical groove 482, 0.0 > 499 < / RTI > Along the groove 491, a vertex 499 is disposed between points 494 and 495. When this coolant reaches the apex 499 of the groove 491, the coolant flow direction through the groove 491 generally changes in a direction through the helical groove 482 and the coolant flows toward the outlet 498 And merged at the fourth point 495. Specifically, at the third point 494, an opening toward the auxiliary coolant groove 491 is oriented relative to the helical groove 482 to receive the liquid coolant in the pressurized state. At the fourth point 495 the opening from the auxiliary coolant groove 491 is oriented relative to the helical groove 482 to facilitate the merging of a small portion and a large portion of the liquid coolant flow along the flow path 480 .

As shown, the liquid coolant flow path 480 is formed by the primary portion 482 and the secondary portion 490, 491 of the fluid channel 478. The first and second points 492 and 493 are fluidly connected in parallel through the secondary portion 490 of the fluid channel and the primary portion 482 of the fluid channel. The third and fourth points 494 and 495 are fluidly connected in parallel through the secondary portion 491 of the fluid channel and the primary portion 482 of the fluid channel. Thus, in the machine 440, the flow path 480 is formed by the helical grooves 482 and the auxiliary coolant grooves 490, 491.

The axially inward end of the first coolant fitting 454 is fluidly connected to the port 512 at the axial end of the cylindrical jacket 470 in front of the machine 440, The gasket or seal 513 seals the engagement between the jacket 470 around the port 512 and the front cover 460. The port 512 is fluidly connected to the inlet 486 of the fluid channel 478. The liquid coolant in the pressurized state is introduced into the machine 440 through the coolant inlet 454 and flows into the fluid channel 478 through the port 512 and the inlet 486. [

A generally cylindrical jacket 470 has an internal volume and an axial end 500 that at least partially surrounds the rear of the machine 440. The axial end 500 of the jacket partially surrounds the inner volume of the jacket, with the rotor 42 and the stator 44 disposed therein. The fluid chamber 502 is formed by the wall 504 of the axial end 500 of the jacket and the fluid chamber 502 is fluidly connected to the fluid channel 478. The wall 504 of the fluid chamber 502 and the rear cover 458 extend between the first and second openings 508 and 510 and define a flow path 480 for the liquid coolant passing through the machine 440 To form a substantially annular fluid passage (506) that forms an annulus. The first opening 508 of the fluid passage 506 is fluidly connected to the outlet 488 of the fluid channel 478. The liquid coolant contained within the fluid passageway 506 is directed through the passageway 506 into the second opening 510 in an annular direction about the central axis 64 along the flow path 480. The second opening 510 is fluidly connected to the axially inward end of the second coolant fitting 456, which is the coolant outlet from the machine 440. The gasket or seal 514 seals the engagement between the jacket 470 and the rear cover 458 to prevent leakage of the liquid coolant from the fluid passageway 506. Alternatively, the second opening 508 of the fluid chamber 502 may be disposed on the cylindrical outer wall of the jacket 470 and the second coolant fitting 456 may be disposed on the rear cover 458 Rather than being fixed to the outer wall. Alternatively, the port 512 may be disposed on the cylindrical outer wall of the jacket 470 and the first coolant fitting 454 may be secured to the front cover 460, as described above and shown in the figures, It fits into the outer wall. In such alternative, non-illustrated embodiment (s), the coolant inlet and outlet fittings extend radially from the machine (440) rather than being supported by, and extending axially from, the front and rear covers (460, 458) do.

A cavity 516 is defined which is defined by the axial end wall 504 of the jacket toward the radially inward side of the annular fluid chamber 502. The cavity 516 is substantially enclosed by the fluid chamber 502 as in the machine 40 of the first embodiment and the cavity 516 and the chamber 502 are in contact with each other through a wall 504 separating them, . A heat source 518 in the form of a power electronics module 520, which may resemble the power electronics 120 of the machine 40 in the cavity 516 and in conductive thermal communication with the wall 504, is disposed. The shaft rear bearing 69 supported in a bearing mounting portion 522 defined by the wall 504 of the axial end 500 of the jacket is another heat source 518 of the machine 440.

The heat transferable from the heat source (s) 518 through the axial end wall 504 of the jacket can be convectively transferred to the liquid coolant along the flow path 480 in the fluid path 506. Heat from the stator 444 and the additional heat source (s) 518 (e.g., power electronics module 520 and / or rear bearing 69) is then transferred to the cylindrical wall of the jacket 470 and to the axial May be convectively delivered to the liquid coolant through the end portion (500).

The flow path 480 for the liquid coolant passing through the machine 440 begins at the first coolant fitting 454 and proceeds through the fluid channel 478 and through the annular fluid path 506 Lt; RTI ID = 0.0 > 456 < / RTI > More specifically, the liquid coolant received through the coolant inlet 454 and port 512 into the machine 440 enters the fluid distribution channel 478 through the inlet 486 and enters a point 492 near the inlet 486 ). A large portion of the branched flow follows the primary portion of the fluid channel 478 along the helical groove 482 and simultaneously extends circumferentially about the central axis 64 and axially in a direction along the central axis, A minor portion of the flow follows the secondary portion of the fluid channel 478 along the secondary coolant groove 490 while the secondary portion extends at points 492 and 493 across the region 496 and spaced along the helical groove 482 . The branched flow is coupled at point 493 and the integrated refrigerant flow continues along spiral groove 482 to point 494 where it is again branched. A large portion of the branched flow follows the primary portion of the fluid channel 478 along the helical groove 482 and simultaneously continues in the circumferential direction about the central axis 64 and axially in the direction along the central axis A minor portion of the branched flow follows a secondary portion of the fluid channel 478 along the secondary coolant groove 491 that extends across the region 497 and into a point 494 , 495, respectively. The branched flow is coupled at point 495 near the outlet 488 and the integrated refrigerant flow continues through outlet 488 to the first opening 508 of the fluid passage 506. The flow path 480 continues in an annular direction around the cavity 516 toward the second opening 510 of the fluid path and then exits the machine 440 through the coolant outlet 456. 35 and 36, the flow path 480 for the liquid coolant passing through the machine 440 is indicated by the directional arrow.

The following is a list of preferred embodiments according to the present disclosure.

1. A liquid-cooled rotary electric machine,

A stator having a central axis;

A rotor surrounded by a stator and rotating about a stator about a central axis;

A jacket having an interior volume in which the stator and the rotor are disposed, surrounding the stator and in an electrothermal-conductive relationship with the stator, and forming a radially outer heat transfer surface with respect to the central axis; And

Fluid channel with inlet and outlet

Wherein the fluid channel extends between an inlet and an outlet of the fluid channel and traverses the heat transfer surface of the jacket and the fluid channel forms a flow path for the liquid coolant passing through the electric machine, And extends in a direction substantially parallel to the central axis between the inlet and the outlet of the fluid channel,

Wherein the flow path for the liquid coolant passing through the electrical machine proceeds in opposite directions parallel to the central axis when crossing the heat transfer surface.

2. The preferred embodiment 1, further comprising a sleeve disposed about the jacket and defining a radially inner coolant receiving surface with respect to the central axis, wherein the fluid channel is disposed between the heat transfer surface of the jacket and the receiving surface of the sleeve Phosphorus liquid rotary electric machine.

3. The liquid-refrigerated rotary electric machine as in any of the embodiments 1 or 2, wherein the flow path extends continuously in a substantially circumferential direction about a central axis.

4. In any of the preceding preferred embodiments, the flow path formed by the fluid channel extends in at least one direction parallel to the central axis independently of extending substantially circumferentially about the central axis Phosphorus liquid rotary electric machine.

5. The liquid refrigerated rotary electric machine according to claim 4, wherein the flow path formed by the fluid channel extends in both directions independently of extending substantially circumferentially about the central axis and independently of the parallel to the central axis.

6. The fluid channel according to any of the preceding preferred embodiments,

A plurality of substantially annularly extending first fluid channel portions each having opposite ends; And

A plurality of second fluid channel portions < RTI ID = 0.0 >

Each first fluid channel portion extending substantially circumferentially about a central axis along each first fluid channel portion between respective opposite ends thereof and the plurality of first fluid channel portions extending along an axis And wherein the flow path travels along each second fluid channel portion in a direction parallel to the central axis.

7. The liquid refrigerant rotary electric machine of claim 6, wherein each of the plurality of second fluid channel portions is in fluid communication with axially adjacent ends of the pair of first fluid channel portions.

8. The liquid refrigerated rotary electric machine as in any of the embodiments 6 or 7, wherein the flow path is axially advanced in a common direction parallel to the central axis along each of the plurality of second fluid channel portions.

9. A method as in any one of embodiments 6-8 wherein the ends of a pair of first fluid channel portions fluidly connected by the second fluid channel portion are substantially radially aligned about a central axis, Electric machine.

10. In any one of embodiments 6-9, each first fluid channel portion extends between an opposing inlet end and an outlet end, and each second fluid channel portion has an inlet of a pair of first fluid channel portions And wherein the plurality of first fluid channel portions are fluidly connected to each other continuously through the plurality of second fluid channel portions.

11. The liquid refrigerated rotary electric machine of embodiment 10 wherein the inlet end and the outlet end of a pair of first fluid channel portions fluidly connected by the second fluid channel portion are axially adjacent to each other.

12. The reactor of embodiment 11 wherein the inlet end and the outlet end of the plurality of first fluid channel sections are substantially radially aligned about the central axis and between the axially adjacent first fluid channel sections about the central axis Alternating in a parallel direction.

13. A fluid channel as in any one of embodiments 6-12, wherein the fluid channel includes a third fluid channel portion having opposite ends and extending in a direction generally parallel to the central axis, Wherein one end of the plurality of first fluid channel portions is fluidly connected to one end of the third fluid channel portion and the other end of the third fluid channel portion is disposed between the fluid channel inlet And fluidly connected to one of the fluid channel outlets.

14. The liquid refrigerated rotary electric machine of embodiment 13 wherein the one end of the first of the plurality of first fluid channel sections is fluidly connected to the other of the fluid channel inlet and the fluid channel outlet.

15. In preferred embodiments 13 or 14, the fluid channel inlet and outlet are in fluid communication with each other through a plurality of interconnecting fluid channel portions comprised of first, second, and third fluid channel portions, The fluid channel portions being fluidly connected to each other in a continuous manner.

16. A fluid channel as in any one of embodiments 6-15, wherein the fluid channel comprises a third fluid channel portion fluidly connected to one end of the plurality of first fluid channel portions, Wherein progression of the flow path along the third fluid channel portion is opposite to progression along the second fluid channel portion.

17. The liquid refrigerated rotary electric machine of embodiment 16 wherein the flow path progresses in a common direction parallel to the central axis along all of the second fluid channel portions.

18. The fluid-cooled rotary electric machine according to any one of the preceding preferred embodiments, wherein both the fluid channel inlet and outlet are arranged in the same direction along the central axis from the rotor.

19. A liquid cooling method for rotating electrical machines,

Comprising the steps of causing a flow of liquid coolant along a flow path formed by a fluid channel to intersect a generally cylindrical heat transfer surface disposed about an axis, the flow path extending substantially circumferentially about an axis, And the fluid channel outlet in a direction parallel to the axis in opposite directions.

20. The method as recited in embodiment 19 wherein the extension of the flow path in a substantially circumferential direction about the axis is independent of the progression of the flow path in at least one direction parallel to the axis.

21. A liquid-cooled rotary electric machine,

A stator having a central axis;

A rotor surrounded by a stator and rotating about a stator about a central axis;

A generally cylindrical jacket having an opposite axial end and an internal volume in which the stator and rotor are disposed and surrounding the stator and in an electrothermal communication relationship with the stator and forming a radially outer heat transfer surface with respect to the central axis; And

Fluid channel across heat transfer surface

Wherein the fluid channel defines a flow path for the liquid coolant passing through the machine and has first and second fluid channel portions, the first fluid channel portion extending in a direction parallel to the central axis Wherein the first fluid channel portion has an opposite end that defines a fluid channel inlet and a fluid channel outlet, respectively, between which fluid channels extend,

Wherein the first and second fluid channel portions are interconnected at spaced points along the first fluid channel portion and one of the spaced interconnecting points is proximate to one of the fluid channel inlet and outlet, Wherein the first fluid channel portion includes an area not crossing the channel portion and the region is disposed between the jacket axial end portion and the first fluid channel portion and the second fluid channel portion extends into the region between the interconnecting points for the first fluid channel portion. Whereby the second fluid channel portion traverses the region and heat can be convectively transferred from the region along the flow path to the liquid coolant.

22. The liquid-refrigerated rotary electric machine of embodiment 21 wherein the fluid channel inlets and outlets are spaced apart in a direction parallel to the central axis.

23. The method as in any of the embodiments 21-22, wherein the first fluid channel portion extends substantially circumferentially about a central axis between the fluid channel inlet and the outlet, and extends about an axis of the first fluid channel portion, And the proceeding in a direction parallel to the axis of rotation is interdependent.

24. In any of the embodiments 21-23, the first fluid channel portion is substantially helical such that the first fluid channel portion extends substantially circumferentially about a central axis and is substantially parallel to the central axis Lt; RTI ID = 0.0 > electric machine. ≪ / RTI >

25. The method as in any one of embodiments 21-24, wherein the first and second fluid channel portions each form a primary and secondary fluid channel portion, and wherein the fluid channel is disposed along the flow path through each of the primary and secondary fluid channel portions. The liquid coolant being adapted to transfer a relatively large portion and a small portion of the liquid coolant.

26. In any of embodiments 21-25, the fluid channel defines a flow path that is diverged between interconnecting points spaced along the first fluid channel portion, the fluid channel extending along the first fluid channel portion And a pair of second fluid channel portions that are each in fluid communication with the first fluid channel portion at respective spaced interconnecting points, wherein the first fluid channel portion extends between the pair of second fluid channel portions, Wherein the channel forms a flow path having alternating branched and non-branched portions between the fluid channel inlet and the outlet.

27. In preferred embodiment 26, each of the two regions of the heat transfer surface across which the first fluid channel portion does not intersect is crossed by the second fluid channel portion, and each region extends between the jacket axial end portion and the first fluid channel portion And each second fluid channel portion extends into a respective region between respective interconnecting points for the first fluid channel portion such that a second fluid channel portion traverses each region and the heat flows from the two regions, Wherein the liquid refrigerant can be convectively conveyed along the furnace to the liquid coolant.

28. In any of the embodiments 21-27, the fluid channel is configured to direct separate portions of the liquid coolant flow that are conveyed along the first and second fluid channel portions to a liquid coolant flow path along the flow path between the fluid channel inlet and outlet, To thereby combine the integrated flow of the rotating electrical machine.

29. In any of embodiments 21-28, the flow path formed by the fluid channel is repeatedly branched and reintegrated between the fluid channel inlet and the outlet, the first fluid channel section does not cross, Wherein the branched portion of the flow path is extended along each second fluid channel portion that intersects the region of the heat transfer surface disposed between the end portion and the first fluid channel portion such that heat is generated by the fluid channel from the plurality of regions Wherein the liquid refrigerant can be convectively conveyed along the furnace to the liquid coolant.

30. The liquid refrigerated rotary electric machine as in any one of embodiments 21-29, wherein in the direction parallel to the central axis, the rotor is disposed between the fluid channel inlet and the outlet.

31. The liquid-refrigerated rotary electric machine as in any one of embodiments 21-30, wherein the interconnecting points spaced along the first fluid channel portion are spaced in a direction parallel to the central axis.

32. The liquid-refrigerated rotating electric machine of embodiment 31 wherein the interconnecting points spaced along the first fluid channel portion are aligned substantially radially with respect to the central axis.

33. The liquid-refrigerated rotary electric machine as in any one of embodiments 21-32, wherein the interconnecting points spaced along the first fluid channel portion are substantially radially aligned with respect to a central axis.

34. In any of embodiments 21-33, wherein one of the interconnecting points spaced along the first fluid channel portion and the fluid channel inlet or outlet is substantially radially aligned with respect to the central axis, Rotary electric machine.

35. The method as in any embodiments 21-34, wherein the first and second fluid channel portions are interconnected at an acute angle in at least one of the interconnecting points spaced along the first fluid channel portion, And the two fluid channel portions converge or diverge along the flow path at the respective interconnecting points, respectively.

36. In any of the embodiments 21-35, the second fluid channel portion is configured such that the direction of the flow path portion along the second fluid channel portion is approximately coincident with the direction of the flow path portion along the first fluid channel portion Thereby forming a vertex that changes direction.

37. In a preferred embodiment 36, the direction of the flow path along the second fluid channel portion between the apex and the fluid channel inlet or near the interconnecting point is defined as the distance between the first and second spaced interconnecting points Lt; RTI ID = 0.0 > 1 < / RTI > fluid channel portion.

38. The liquid-cooled rotary electric machine as in embodiment 37 wherein the generally opposite flow path direction is about a central axis.

39. The liquid-cooled rotary electric machine as in any one of embodiments 36-38, wherein the apex is disposed approximately centrally along the length of the second fluid channel portion between spaced interconnecting points.

40. A liquid cooling method for rotating electrical machines,

A flow of liquid coolant that follows a flow path formed by a fluid channel between a fluid channel inlet and an outlet, the flow of liquid coolant extending around the axis and being disposed about the axis along a first fluid channel portion extending in a direction parallel to the axis Traversing the heat transfer surface;

Along a second fluid channel portion extending into a region between a point along a first fluid channel portion proximate the fluid channel inlet or outlet and another point along the first fluid channel portion such that the first fluid channel portion does not cross, Across a region of the heat transfer surface disposed between the axial end of the first fluid channel portion and the first fluid channel portion; And

Convectively transferring heat from the region to the liquid coolant along the flow path

And cooling the cooling water.

41. A liquid-cooled rotary electric machine,

Coolant inlet and coolant outlet;

A stator having a central axis;

A rotor surrounded by a stator and rotating about a stator about a central axis;

A jacket for forming a heat transfer surface in conductive heat communication with a stator, the jacket having an opposite axial end, an inner volume in which the stator and rotor are disposed, and an axial end having a wall, A jacket partially surrounded by the end portion;

A fluid channel across the heat transfer surface of the jacket between the axial ends of the jacket;

A fluid passage formed by the axial end wall of the jacket and in fluid communication with the fluid channel and a flow of liquid coolant through the machine formed by fluid passages and fluid channels between the coolant inlet and the coolant outlet; And

A heat source in conductive thermal communication with the axial end wall of the jacket

Wherein at least a portion of the heat transferable between the heat source and the fluid passage is convectively transferable between the axial end wall of the jacket and the liquid coolant along the flow path.

42. In preferred embodiment 41, the fluid pathway has first and second openings extending between the flow paths of liquid coolant through the machine, the fluid channel and the fluid pathway having one of the first and second openings Wherein the fluid is connected to each other through a plurality of through-holes.

43. The liquid-cooled rotary electric machine of embodiment 42 wherein the other of the first and second openings is fluidly connected to one of a coolant inlet and a coolant outlet.

44. In preferred embodiment 43, the axial end wall of the jacket forms an isolated port from the fluid path, the fluid channel is fluidly connected to the port, and the other of the coolant inlet and the coolant outlet is fluidly connected to the port Liquid rotating electric machine.

45. The liquid-refrigerated rotary electric machine as in any one of embodiments 42-44, wherein the first and second openings are disposed at opposite ends of the fluid path along the flow path.

46. The liquid-refrigerated rotary electric machine as in any one of embodiments 42-45 wherein the flow path is generally helical between the first and second openings.

47. The liquid-refrigerated rotary electric machine as in any one of embodiments 42-45, wherein the flow path is substantially annular between the first and second openings.

48. The liquid-refrigerated rotary electric machine as in any one of embodiments 41-47, wherein the heat source is axially disposed adjacent the axial end wall of the jacket with respect to the central axis.

49. The liquid-refrigerated rotary electric machine as in any one of embodiments 41-48, wherein the heat source is radially disposed adjacent the axial end wall of the jacket with respect to the central axis.

50. The liquid-refrigerated rotary electric machine as in any one of embodiments 41-46, wherein the axial end of the jacket completely surrounds the internal volume at one jacket axial end.

51. The liquid refrigerated rotary electric machine as in any one of embodiments 41-46, wherein the fluid passageway and the heat source do not overlap in the axial direction.

52. The liquid-refrigerated rotary electric machine as in any one of embodiments 41-51, wherein the rotating electrical machine comprises a power electronics and the heat source comprises a power electronics.

53. The pulley as in embodiment 52 wherein the rotating electrical machine is disposed over the jacket axial end and includes a cover defining a fluid passageway and the power electronics is disposed between the cover and the jacket axial end wall, Electric machine.

54. The rotating electrical machine as in any one of embodiments 41-51, comprising a bearing supported by a jacket axial end, the rotor being supported within a jacket inner volume by a bearing, the heat source comprising a bearing Phosphorus liquid rotary electric machine.

55. The liquid-refrigerated rotary electric machine as in any one of embodiments 41-54, wherein the heat source is disposed axially between the rotor and the fluid passageway.

56. The liquid-refrigerated rotary electric machine as in any one of embodiments 41-55, wherein a portion of the fluid passageway extends toward a radially outer side of the heat source with respect to a central axis.

57. The fluidized-bed as in any one of embodiments 41-56, further comprising a removable cover defining a fluid path, wherein the fluid path is disposed between the rotor and the cover in a direction parallel to the central axis Electric machine.

58. The liquid-cooled rotary electric machine as in embodiment 57 wherein the heat source is disposed axially between the cover and the jacket axial end wall.

59. The liquid-refrigerated rotary electric machine according to any one of embodiments 41-57, wherein the heat source is disposed axially between the rotor and the jacket axial end.

60. A liquid cooling method for a rotary electric machine,

A jacket axial end portion that partially circumscribes an inner volume that is continuously fluidly connected to the fluid channel and is disposed with the stator and rotor disposed along the fluid channel across the heat transfer surface of the jacket in conductive thermal communication with the stator surrounding the rotor, Transferring the liquid coolant along a fluid passage formed by the liquid coolant; And

From the heat source from the stator through the heat transfer surface and from the heat source in conductive thermal communication with the wall at the end of the jacket axial direction, the fluid channel extending between the coolant inlet of the machine and the coolant outlet, In a convection manner

And cooling the cooling water.

61. A liquid-cooled rotary electric machine,

Coolant inlet and coolant outlet;

A stator having a central axis;

A rotor surrounded by a stator and rotating about a stator about a central axis;

A jacket for forming a heat transfer surface in conductive heat communication with a stator, the jacket having an opposite axial end, an inner volume in which the stator and rotor are disposed, and an axial end having a wall, A jacket partially surrounded by the end portion;

A fluid channel across the heat transfer surface of the jacket between the axial ends of the jacket;

A fluid passage formed by the axial end wall of the jacket and in fluid communication with the fluid channel and a flow of liquid coolant through the machine formed by fluid passages and fluid channels between the coolant inlet and the coolant outlet; And

A heat source substantially enclosed by the fluid passageway in an imaginary plane perpendicular to the central axis and in conductive thermal communication with the axial end wall of the jacket,

Wherein at least a portion of the heat transferable between the heat source and the fluid passage is convectively transferable between the axial end wall of the jacket and the liquid coolant along the flow path.

62. In preferred embodiments 41 or 61, the fluid passages have first and second openings extending between the flow passages, wherein the fluid channels and the fluid passages are fluidly connected to each other through one of the first and second openings Liquid rotating electric machine.

63. The liquid-cooled rotary electric machine as in any of the embodiments 42-62, wherein the other of the first and second openings is fluidly connected to one of a coolant inlet and a coolant outlet.

64. In preferred embodiments 43-63, the axial end wall of the jacket forms an isolated port from the fluid path, the fluid channel is fluidly connected to the port, and the other of the coolant inlet and coolant outlet is fluidly connected to the port Liquid rotating electric machine.

65. The liquid-refrigerated rotary electric machine as in any one of embodiments 42-44 or 62-64, wherein the first and second openings are disposed at opposite ends of the fluid path along the flow path.

66. The liquid-refrigerated rotary electric machine as in any one of embodiments 42-45 or 62-65, wherein the flow path is substantially S-shaped between the first and second openings.

67. The liquid-refrigerated rotary electric machine as in any one of embodiments 42-45 or 62-65, wherein the flow path is substantially annular between the first and second openings.

68. The liquid-cooled rotary electric machine as in any of the embodiments 47-67, wherein the substantially annular flow path substantially surrounds the heat source.

69. In preferred embodiment 61, the machine includes first and second heat sources, wherein the generally S-shaped flow path substantially surrounds each of the first and second heat sources in an imaginary plane. .

70. The liquid-refrigerated rotary electric machine as in embodiment 69, wherein the pair of heat sources are separated by a fluid passage.

71. The liquid-cooled rotary electric machine of embodiment 69 wherein at least one of the first and second heat sources comprises a power electronics.

72. The liquid-cooled rotary electric machine as in any of the embodiments 52 or 71, further comprising a cover removably attached to the jacket axial end and defining a fluid path, wherein the power electronics is mounted on a removable cover.

73. The machine tool as in any of the embodiments 41-45 or 61-71, further comprising a cover removably attached to the jacket axial end and defining a fluid passageway, the heat source comprising a power electronics And an electric motor.

74. The liquid-cooled rotary electric machine as in embodiment 61 wherein the heat source comprises a power electronics and the jacket axial end receives a power electronics and forms a cavity in a conductive thermal relationship with the fluid passageway.

75. The preferred embodiment 74, further comprising a pair of heat sources each including a power electronics, the jacket axial end defining a pair of cavities in an electrothermal-conductive relationship and in fluid communication with the fluid passages, Wherein the pair of heat sources are disposed in a pair of cavities, each cavity being substantially surrounded by a fluid passageway in an imaginary plane.

76. In preferred embodiments 74 or 75, the jacket axial end wall forms a cavity and the fluid passageway substantially surrounds the cavity so that heat transferable from the power electronics to the fluid passageway through the jacket axial end wall And is capable of being convectively transferred to the liquid coolant along a flow path formed by the fluid passageway.

77. The liquid-refrigerated rotating electric machine as in any one of embodiments 74-76, wherein the fluid passageway is substantially annular and extends substantially circumferentially about the central axis and the cavity.

78. The rotor of any of embodiments 41-45 or 61-71, further comprising a cover defining a fluid passage, wherein the fluid passage is disposed between the rotor and the cover in a direction along the central axis, Electric machine.

79. The liquid refrigerated rotary electric machine of embodiment 78 wherein a cavity is formed by the jacket axial end wall to receive the heat source and the heat source is disposed between the rotor and the cover in a direction along the central axis.

80. A liquid cooling method for a rotating electric machine,

A fluid channel extending transversely to the heat transfer surface of the jacket in an electrothermal-conductive relationship with the stator surrounding the rotor about the central axis and partially surrounding the inner volume fluidly connected in series to the fluid channel, Conveying the liquid coolant along a fluid path defined by the jacket axial end; And

From a heat source communicating with the wall of the jacket axial end through the heat transfer surface from the stator substantially along a flow path extending between the coolant inlet and the coolant outlet of the machine and substantially surrounding the heat source in a virtual plane perpendicular to the central axis Convection of heat to the liquid coolant

And cooling the cooling water.

Although the illustrative embodiments have been disclosed above, the present disclosure is not limited to the disclosed embodiments. Instead, this application is intended to cover any variations, uses, or adaptations of the present disclosure utilizing its general principles. This application is also intended to cover such departures from the present disclosure as come within known or customary practice in the art to which this disclosure pertains and which fall within the limits of the appended claims.

Claims (20)

A liquid-cooled rotary electric machine (40, 140, 240, 340)
A stator 44 having a central axis 64;
A rotor 42 surrounded by the stator 44 and rotating about the stator 44 about the central axis 64;
And has an internal volume in which the stator 44 and the rotor 42 are disposed and which surrounds the stator 44 and is in an electrothermal and thermal communication relationship with the stator and forms a radially outer heat transfer surface 74 with respect to the central axis 64 , Jackets (70, 170, 270); And
A fluid channel (78) having an inlet (86) and an outlet (88)
The fluid channel 78 extending between the inlet 86 and outlet 88 of the fluid channel and across the heat transfer surface 74 of the jacket and the fluid channel 78 extending between the electrical machine 40, 180, 280 for the liquid coolant passing through the fluid passages (240, 340), the flow path extending substantially circumferentially about the central axis (64) And travels in a direction parallel to the central axis 64 between the outlets 88,
Flow paths 80, 180 and 280 for the liquid coolant passing through the electrical machines 40, 140, 240 and 340 travel in opposite directions parallel to the central axis 64 when traversing the heat transfer surface 74 Liquid rotating electric machine. 7. The assembly of claim 1, further comprising a sleeve (72) disposed about the jacket (70, 170, 270) and defining a radially inner coolant receiving surface (76) with respect to the central axis (64) Is disposed between the heat transfer surface (74) of the jacket and the receiving surface (76) of the sleeve. 3. The liquid-cooled rotary electric machine according to claim 1 or 2, wherein the flow paths (80, 180, 280) extend continuously in a substantially circumferential direction about a central axis (64). 4. A device according to any one of claims 1 to 3, wherein the flow paths (80, 180, 280) formed by the fluid channels (78) extend substantially circumferentially about the central axis (64) And in at least one direction parallel to the central axis (64). 5. The apparatus of claim 4, wherein the flow paths (80,180, 280) formed by the fluid channels (78) are substantially parallel to the central axis (64) independently of extending substantially circumferentially about the central axis And wherein the liquid-cooled rotary electric machine is operated in both directions. 6. A device according to any one of claims 1 to 5, wherein the fluid channel (78)
A plurality of substantially annularly extending first fluid channel portions (90) each having an opposite end (94); And
A plurality of second fluid channel portions 92 each fluidly connecting an end 94 of a pair of first fluid channel portions 90,
Each first fluid channel portion 90 extending substantially circumferentially about a central axis 64 along each first fluid channel portion 90 between each opposing end 94, A plurality of first fluid channel portions 90 are axially distributed along a central axis 64 and a plurality of flow channels 80, 180 and 280 are disposed along a central axis 64 along each second fluid channel portion 92. [ And wherein the liquid-cooled rotary electric machine is operated in a direction parallel to the direction of rotation. 7. The liquid-refrigerated rotary electric machine of claim 6 wherein each of the plurality of second fluid channel portions (92) is in fluid communication with an axially adjacent end (94) of a pair of first fluid channel portions (90). 8. A method according to claim 6 or 7, wherein the flow paths (80, 180, 280) are axially advanced along a respective plurality of second fluid channel portions (92) in a common direction parallel to the central axis Phosphorus liquid rotary electric machine. 9. A method according to any one of claims 6 to 8, wherein the ends (94) of a pair of first fluid channel portions (90) fluidly connected by the second fluid channel portion (92) And wherein the first and second electrodes are substantially radially aligned. 10. A method according to any one of claims 6 to 9, wherein each first fluid channel portion (90) extends between an opposing inlet end and an outlet end (94) and each second fluid channel portion (92) The first fluid channel portion 90 is fluidly connected to the inlet end and the outlet end 94 of the pair of first fluid channel portions such that the plurality of first fluid channel portions 90 are fluidly connected to each other through the plurality of second fluid channel portions 92, Wherein the liquid-cooled rotary electric machine is connected to the electric motor. 11. The fluid control device of claim 10, wherein the inlet end and outlet end (94) of a pair of first fluid channel portions (90) fluidly connected by the second fluid channel portion (92) are axially adjacent to each other, machine. 12. The method of claim 11, wherein the inlet and outlet ends (94) of the plurality of first fluid channel sections (90) are substantially radially aligned at a central axis periphery (64) (90) in a direction parallel to the central axis (64). 13. The device of any one of claims 6 to 12, wherein the fluid channel (78) includes a third fluid channel portion (96) having an opposite end and extending in a direction generally parallel to the central axis (64) 3 fluid channel portion 96 is disposed between opposing ends 94 of each first fluid channel portion 90 and one end 94 of one of the plurality of first fluid channel portions 90 Fluid channel portion 96 is fluidly connected to one end of the third fluid channel portion 96 and the other end of the third fluid channel portion 96 is fluidly connected to one of the fluid channel inlet 86 and the fluid channel outlet 88. [ Rotary electric machine. 14. The method of claim 13, wherein one end (94) of the first of the plurality of first fluid channel portions (90) is fluidly connected to the other of the fluid channel inlet (86) and the fluid channel outlet Liquid rotating electric machine. 15. A method according to claim 13 or 14, wherein the fluid channel inlet (86) and the outlet (88) comprise a plurality of interconnecting fluid channels (90, 92, 96) comprising first, Wherein the plurality of interconnecting fluid channel portions (90, 92, 96) are in fluid communication with each other in a continuous manner. 16. A device according to any one of claims 6 to 15, wherein the fluid channel (78) comprises a third fluid channel portion (96) fluidly connected to one end (94) of one of the plurality of first fluid channel portions (90) And the progress of the flow path 80, 180, 280 along the third fluid channel portion 96 in a direction parallel to the central axis 64 is opposite to the progression along the second fluid channel portion 92 Liquid rotating electric machine. The liquid-cooled rotary electric machine according to claim 16, wherein the progress of the flow paths (80, 180, 280) is in a common direction parallel to the central axis (64) along both of the second fluid channel portions (92). 18. A device according to any one of the preceding claims, wherein both the fluid channel inlet (86) and the outlet (88) are arranged in the same direction along the central axis (64) Electric machine. As a liquid cooling method for rotating electrical machines (40, 140, 240, 340)
Comprising causing a flow of liquid coolant along a flow path (80,180, 280) formed by a fluid channel (78) to traverse a generally cylindrical heat transfer surface (74) disposed about an axis (64) The flow passages 80,180 and 280 extend substantially circumferentially about the axis 64 and extend in opposite directions parallel to the axis 64 between the fluid channel inlet 86 and the fluid channel outlet 88 Wherein the liquid cooling method comprises: 20. The method of claim 19, wherein the extension of the flow path (80,180, 280) in a substantially circumferential direction about the axis (64) comprises a flow path (80,180, 280) in at least one direction parallel to the axis ) Of the rotating electrical machine.

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