Patent Application
20060165523
This invention relates to fluid pumps and, more particularly, to centrifugal coolant pumps for use with an internal combustion engines.
Centrifugal-type automotive water pumps are known in the art for pumping coolant through internal combustion engines. However, improvements in performance and efficiency are desired.
The present invention includes design features that can provide a smaller water pump with improved flow performance.
The pump includes a housing defining an internal chamber having an axial inlet passage connecting with a generally radial passage having an outlet to a volute. A bearing supported shaft, rotatable on an axis, is carried in the housing. The shaft extends from the chamber axially through the housing and is connected with a drive member at an opposite end of the housing. An impeller is carried on the shaft within the chamber. The impeller has a conical rear shroud sloping away from the axial inlet.
A front surface of the shroud carries long and short vanes operable to impel fluid from the axial inlet to the volute. The long vanes extend forward into the axial inlet and induce coolant pre-rotation in the inlet to improve pump efficiency and reduce the likelihood of cavitation. The long vanes also extend outward to the outlet to impel fluid from the axial inlet to the volute. The short vanes extend to the outlet between and parallel with outer portions of the long vanes. The vanes are also curved backward, opposite the direction of impeller rotation, to maximize flow efficiency.
A shaft seal, sealingly engaging the shaft, is carried in the housing and received within a recessed rear portion of the conical shroud. The seal is thus nested within the profile of the impeller, thereby reducing the axial length of the pump.
The axial inlet passage is defined by a conical side wall, increasing in diameter from an inlet opening to a radius joining with a sloped (preferably conical) front wall. The sloped front wall is spaced adjacent front surfaces of the impeller vanes and slopes rearward toward the outlet, generally parallel to the slope of the impeller. The combination of the conical side wall having a radius joining with the sloped front wall reduces coolant turbulence and the likelihood of coolant flow separation at high speeds and flows to inhibit cavitation. The reduction in turbulence also improves efficiency.
These and other features and advantages of the invention will be more fully understood from the following description of certain specific embodiments of the invention taken together with the accompanying drawings.
Referring first to
As shown in
The vanes 42, 44 illustrated in
If desired, the shroud of the impeller may have pressure balancing holes 46 that extend through the shroud to equalize fluid pressures adjacent the front surface 40 and the rear recess 39 of the impeller 36.
The axial inlet passage 16 is defined by a conical wall 48 of the housing 12, increasing in diameter from an inlet opening 50 to a radius 52, joining wall 48 with a sloped front wall 54 of the housing 12. The sloped front wall 54 is spaced adjacent front edges 55 of the vanes 42, 44 of the impeller 36. The front wall 54 slopes rearward, away from the inlet opening 50, to the outlets 22, 24 and generally parallel to the slope of the impeller 36. The combination of the conical wall 48 and the radius 52 joining with the sloped front wall 54 reduces turbulence and the likelihood of coolant flow separation at high speeds and flows, to inhibit pump cavitation. This reduction in turbulence also improves the efficiency of the pump 10.
A shaft seal 56 is carried in the housing 12 adjacent the shroud 38 of the impeller 36 to sealingly engage the shaft 28. The seal includes a support ring 58 pressed into a bore of the drive body 13 and a lip seal 60 carried by the ring 58 and engaging the shaft 28 to control coolant leakage. The lip seal 60 is positioned within the rear recess 39 of the shroud 38 to minimize the axial length of the pump 10 by carrying the seal lip within the profile of the impeller.
In operation, a chain or accessory belt, not shown, is connected to the drive member 34 to rotate the shaft 28 and the impeller 36 and operate the pump 10. Alternatively, the shaft 28 may be directly driven by a gear or motor, not shown, engaging the drive member 34.
As the impeller 36 is rotated within the housing 12, fluid is drawn into a center portion of the rotating impeller 36 from the inlet opening 50 and the axial inlet passage 16. The increasing diameter of the conical wall 48 reduces the velocity of fluid flow from the inlet opening 50 to the vanes 42 of the impeller 36. The long vanes 42 of the impeller 36 extend into the axial inlet passage 16 to pre-rotate fluid within the axial inlet passage. This causes the fluid to swirl in the same direction as the rotation of the impeller and reduce the likelihood of cavitaion when the impeller increases in speed.
As the impeller 36 rotates, it generates centrifugal force which pumps the fluid through the outlets 20, 22 to the volutes 24, 26. Fluid entering the inlet 50 is slowed by the increasing diameter of the conical wall 48 and is prerotated and drawn in by the long vanes 42. The large radius and shallow angle smooth flow along the sloped front wall, reducing turbulence and thereby increasing pump efficiency and the likelihood of cavitation.
In the embodiment of
Referring now to
As shown in
A bearing 127 supports a shaft 128, rotatable on an axis 130, and carried in the drive body 113 of the housing 12. The shaft 128 extends axially through the drive body 113 of the housing and mounts a flange 132 with a drive member, such as pulley 134, adjacent an outer end 135 of the housing 112. An impeller 136 is disposed in the chamber 114 and carried on an inner end 137 of the shaft 128.
As shown in
The vanes 142, 144 illustrated in
The shroud of the impeller may be provided with pressure balancing holes 146 that extend axially through the shroud to equalize fluid pressure adjacent the front surface 140 and the rear recess 139 of the impeller 136.
The axial inlet passage 116 is defined by a generally cylindrical wall 149. The passage is made large enough to limit coolant flow to a value low enough to prevent cavitation in the inlet. The passage 116 is joined by a radius 152 with a sloped front wall 154 of the housing 112. The sloped front wall 154 is spaced adjacent front edges 155 of the vanes 142, 144 of the impeller 136. The front wall 154 slopes rearward, away from the inlet passage 116, to the outlets 122, 124 and generally parallel to the slope of the impeller 136. The combination of the large inlet passage 116 with cylindrical wall 149 and the radius 152 joining with the sloped front wall 154 is configured to reduce turbulence and the likelihood of coolant flow separation at high speeds and flows and to inhibit pump cavitation. This reduction in turbulence also improves the efficiency of the pump 110.
A shaft seal 156 is carried in the housing 112 adjacent the shroud 138 of the impeller 136 to sealingly engage the shaft 128. The seal includes a support ring 158 pressed into a bore of the drive body 113 and a lip seal 160 carried by the ring and engaging the shaft 128 to control coolant leakage. The lip seal 60 is positioned within the rear recess 139 of the shroud 138 to minimize the axial length of the pump 110 by carrying the seal lip within the profile of the impeller. Pump length beyond the front wall of the engine is further reduced by using the front wall as the housing inlet cover 114. In this way, the protrusion of the pump is minimized by including only the axial length of the drive body 113 and the protrusion of the shaft 128 beyond the outer end 135 of the housing 112. Alignment of an outer end 164 of the pulley 134 with the shaft end minimizes shaft protrusion by providing for the drive belt, not shown, to align laterally as close as possible with the shaft end.
Operation of the pump 110 is generally similar to that of pump 10. However, pump 110 is more compact, has a lower flow rate than the larger unit and is integrated into the engine front wall (inlet cover 114), so that some of the features are altered to suit the application. In this instance, the vanes 142, 144 are curved backward for efficient fluid flow as the impeller 36 is rotated in a clockwise direction as viewed from the inner end (or front side) of the impeller as shown in
While the invention has been described by reference to certain preferred embodiments, it should be understood that numerous changes could be made within the spirit and scope of the inventive concepts described. Accordingly, it is intended that the invention not be limited to the disclosed embodiments, but that it have the full scope permitted by the language of the following claims.
