CA1039573A - Cooling water pump, preferably for motor car engines - Google Patents
Cooling water pump, preferably for motor car enginesInfo
- Publication number
- CA1039573A CA1039573A CA229,540A CA229540A CA1039573A CA 1039573 A CA1039573 A CA 1039573A CA 229540 A CA229540 A CA 229540A CA 1039573 A CA1039573 A CA 1039573A
- Authority
- CA
- Canada
- Prior art keywords
- pump unit
- bearing
- impeller
- drive member
- seal
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Abstract
ABSTRACT OF THE INVENTION:
A pump unit for liquid-cooled internal combustion engines preferably for vehicle engines includes a pump unit bearing housing, an impeller, and a drive member operatively connected to the impeller to rotate the same, forming a rotatable assembly. Bearing means support the drive member for rotation relative to the housing and a seal is adapted to seal an annular space between the rotatable assembly and the housing. The axial length of the pump unit as measured from the impeller to the oppositely located end of the drive member and the pitch diameter of the bearing are of about the same order of magnitude.
A pump unit for liquid-cooled internal combustion engines preferably for vehicle engines includes a pump unit bearing housing, an impeller, and a drive member operatively connected to the impeller to rotate the same, forming a rotatable assembly. Bearing means support the drive member for rotation relative to the housing and a seal is adapted to seal an annular space between the rotatable assembly and the housing. The axial length of the pump unit as measured from the impeller to the oppositely located end of the drive member and the pitch diameter of the bearing are of about the same order of magnitude.
Description
~03957~
The present invention relates to a pump unit for liquid cooled internal combustion engines, preferably for a motor car engine. The pump in accordance with the invention constitutes in mounted condition a unit in which the components preferably are undetachably united together.
The conventional cooling water pumps are so designed, that they consist of relatively large parts fastened together with screws and such pumps are relatively heavy and space consuming.
According to one aspect of the invention, a pump unit for liquid-cooled internal combustion engines comprises a bearing housing member, an aperture formed therein; a rotatable assembly including an impeller disposed adjacent one side of said housing member and rotatably supported by said housing member and a drive member for rotating said impeller and including a drive pully disposed adjacent the other side of said housing member, said , .~.
assembly including a connecting portion extending through said aperture and connecting said impeller to said drive member; bearing means supporting the drive member for rotation relative to the housing member; and a seal adapted to seal said aperture between said rotatable assembly and said housing member wherein the axial length L of the pump unit as measured from ~he impeller to the oppositely located end of the drive member and the pitch `
diameter Dm of the bearing means are related mathematically by the expres-sion L ~f~ ~ Dm ~ L/~
,: .
-1- ~
, . .
' . - ' ' ' ' ~39573 The advantages of fluid pumps in accordance with the present invention are the following: It is possible to select various materials for this shaftless type of pump. Suitable materials might be aluminum, plastics or pressed metal sheet. In selecting a suitable material, the pump will be cheap and light and has in relationship to the small weight, a good struc-tural strength. The good reliability in operation depends on the fact that there will be less unbalance and smaller masses in the pump components. An important feature of the pump unit of the present invention is its compact design. To this end, since there is no conventional shaft, the bearing of one embodiment of the pump unit is selected with greater pitch diameter and of about the same order of magnitude as the axial length of the pump unit measured from the impeller to the oppositely located end of the drive member.
Such a bearing, preferably of single row deep groove type, or in some cases of double row angular contact type, is simpler and axially more compact. i Additionally, the axial length of one embodiment of the pump unit measured ~ ~`
from the impeller to the outer end of drive member and the outer diameter of the impeller are of the same order of magnitude to provide a compact pump unit. Further, the axial length of the pump unit is of about the same or at most, equal to the diameter of the impeller. A further advantage is the possibility of getting a good sealing effect since the sealing diameter is ;~
very small. The pump unit is so designed that a good ventilating and drying of the bearing is obtained in front of, or behind the same, so that possible fluid particles will not get into contact with the bearing. Regarding an ~ ;
outer-ring-rotated bearing, it is possible to place the seal with its small diameter essentially :. - . : ,, . . .- - - :: ...
.: . ' . . ! . . .
- ' ' , .. .' ' ,' . " '. ~ ' ~ ~ ' ' ' ' ' ' ' .' ' ' ' ' ' ' ' ' ' ' , . ` ' `' ' ~ ' , ' . , ' ' ' , ,, . ~' ' ' " " ''' '. ' " ' ' ' ' , .. . .. . . ' ~L039573 `
in the radial center line of the bearing, whereby a considerable increase in the life of the seal is obtained.
The invention will now be described with reference to the accompanying drawings in which: Figure 1 shows an embodlment of the pump unit with a specially shaped inner-ring-rotated bearing;
Figure 2 shows a modification of the pump unit with an outer-ring-rotated bearing;
Figure 3 is a sectional view of still another embodiment of pump unit in accordance with the present invention; and Figure 4 is a sectional view of a modified form of the pump unit shown in Figure 3.
Referring now to the drawings and particularly to Figure 1 thereof, there is illustrated a pump unit constructed in accordance ~nth the present invention~ the main components of which include a pump unit bearing housing 1~ a bearing 2~ a drive member 3, a rotor or impeller 4~ and a sealing element 5. In the assembly illustrated, the pump unit housing 1 is detachably mounted by suitable means such as screws to the pump housing ~ to support the pump unit assembly in an opening in the pump housing, which may be a conventional volute casing. It is noted that the pump unit may be secured to the pump housing by other means; for example, by a press fit or be formed integrally therewith.
Figure 1 shows a cooling water pump in which the pump lmit bearing housing 1 consists of a relatively thin wall 6 of pressed sheet metal~ die~
casted aluminum or plastics which is fixed to a stronger housing portion 7 suitably of aluminum. In the portion 7, the outer ring 8 of the bearing 2 is fitted by shrinkage fit or otherwise. The inner and of the drive member 3 is of a stepped configuration to define the inner raceway 9 of the bearing and an axially extending seat 13 of smaller diameter than the raceway 9 for the seal S. As illustrated, a space or p~cket for the seal is provided between ~L039S73 the wall 6 of the pump unit housing 1 and the radial leg 30 of the drive member 3 connecting the raceway 9 and seal 13. The rotor 4 is mounted on the radial extension 32 depending from seat 13 by suitable means; for instance~
by welding or riveting. The inner raceway 9 is in the embodiment shown integrated with the drive member 3 of the pump unit, but the raceway might also be shaped in a separate inner ring fitted on the drive member 3 In the embodiment shown, the rolling bodies of the bearing consist of balls and the bearing is provided with a cage 10 of a suitable type. As shown in the figure, the inner ring will be rotated.
The pump unit is in this case driven by a belt from a suitable source of power. For this purpose the drive pulley part 11 of the drive member 3 is profiled on its outer surface as shown at 12. In the embodiment illustrated, the bearing is a single row deep groove ball bearing and the seal 5 is mounted radially inwardly of the pitch circle of the bearing.
Further, in accordance with the present invention, the axial length L of the pump unit measured from the rotor 4 to the outer end of the drive member 3 and the pitch diameter Dm of the bearing are preferably of the same order of magnitude. Additionally, the axial length L of the pump unit and the outer diameter D of the rotor 4 are preferably of the same order of magnitude.
~urther, the axial le~gth L of the pwmp unit may be approximately equal to, or at most, equal to the diameter D of the rotor 4. This arrangement pro-vides a very compact pump unit and facilitates the use of a comparatively simple type of bearing such as the single row deep groove ball bearing illustrated. Further, by this construction, the seal can be located in close proximity to the bearing and will be insensitive to any possible wobbling or warping, and thus have an extended life. Seal failure is one of the more common failures in the water pumps in the automotive field. Additionally, a compact pump unit design offers greater freedom in selection of materials so that the pump unit may be made very economically and of light weight .. . . . .
:' ~ '' ~ '' -' ., .
.
. . .:~ : -' ~
construction. ~o39~73 The various components of the pump unit provide a shaftless assembly wherein the various elements such as the bearing, d~ive member, impeller and pump unit housing preferably form an integral unit which is easily replace-able in the event of pump failure.
In new installations, the separable integral pump unit of the present invention is adapted for use with various pump housing designs thereby providing a standard unit which may be assembled to a plurality of different designed pump housing and therefore has a non-obsolescent characteristicO
Presently, as engine designs are changed, it often necessitates a correspond-ing design change in the entire water pump assembly.
In the pump unit housing 1 tnere is provided a number of large openings 14 intended for ventilating, drying and draining purposes. Through these openings there is obtained a very effective ventilating or draining in front of the bearing. Close to the drive side of the pump there can be applied a fan (not shown here). This can be designed in such a way that the fan is integrated with the drive member of the pump so that a combined fan and drive member is obtained. The fan can, of course, be a separate part fixed to the drive member. ~
In Figure 2 a modiication of the cooling water pump unit is shown --in which, unlike the above mentioned embodiment, the outer ring of the bearing rotates. The parts of the pump unit which are similar to the previously de- ;
scribed embodiment are referenced by the same numerals with the letter "a"
postscript. In this example a conventional bearing is used, for example, a single row deep groove ball bearing, the inner ring 15 of which is fitted on an annular part 16 of the pump unit bearing housing la. The outer ring 17 of the bearing is fitted into a bearing seat 18 in the drive member 3a. The outer surface of the drive pulley part of the drive member is profiled at 19 as in the first embodiment. The drive member is provided with a web portion : , . . .
~039~i73 20 which i5 fixed to a hub portion 21 of the impeller~ by~ for example~ weld-ing. The seal 5a is fitted to a suitable place on the portion 21 in connection with the inner part of the pump unit housing 1~. The seal can also be located in the radial center line of the bearing whereby angular warpings are elimin-ated. The drive member is also in this embodimant provided with large drain-ing/ventilating openings 22.
In the present instance, the axial length L of the pump unit assembly measured from the rotor 4a to the outer end of the drive member 3a, and the pitch diameter D of the bearing are preferably of the same order of magnitude.
10 Additionally, the axial length L of the pump unit and the outer diameter D i of the rotor 4 are preferably of the same order of magnitude. Further, the ~ ~-axial length L of the pump unit may be approximately equal to, or at most, equal to the diameter Dr of the rotor 4. These relationships provide the functional advantages set forth above in connection with the previously de-scribed embodiment. Further, as illustrated, the seal 5a is located closely adjacent the bearing assembly and disposed radially inwardly thereof. To this end, the housing la is provided with an annular recess defining two walls of a pocket for the seal at the juncture of the radial portion 24 of the housing la and the annular part 16. The other walls of the p~-cket, as illus- ;
trated, are defined by the rear face of the impeller and the hub portion 21.
Figure 3 shows another embodiment of pump unit in accordance with ~-the present invention. The elements of the pump unit similar to those of the previously described embodiment, are designated by the same numerals with the letter "b" postscript. Thus the pump unit comprises a pump unit housing lb adapted to be secured by suitable means to the main pump housing H , for example, in the manner described previously, a rotor or impeller 4b, one end of which is disposed interiorly of the pump housing H and is secured to a drive member 3b, which in the present instance has a sheave or pulley formed , ~ . , ~ .
,' ' : - - . .
~039573 integrally therewith for a belt connected to a suitable drive means to rotate the impeller. The drive member 3b mo~mts at its o~lter and remote from the pump unit housing lb, a fan wheel 29 connected at its hub portion 31 in a suitable manner, for example, by screws 34. The bearing 2b in the present instance, is illustrated as a single row deep groove ball bearing comprising an outer ring 17b fitted in the drive member 3b, an inner ring 15b fitted in the pump unit housing lb and a plurality of balls in the annular space between the rings. However, when a fan wheel 29 is provided, a double row angular contact ball bearing is preferred. The drive member is also provided, in -the present instance~ with draining/ventilati~g openings 22b.
In accordance with this embodiment, the axial length L of the pump unit measured from the rotor 4b to the outer end of the drive member 3b and the pitch diameter D of the bearing are preferably of the same order of magnitude. Additionally, the axial length L of the pump unit and the outer diameter D of the rotor 4 are preferably of the same order of magnitude.
Further, the axial length ~ of the pump unit may be approximately equal to~ -or at most, equal to the diameter D of the rotor 4. These relationships provide the functional advantages set forth above in connection with the previously described embodiments. Further as illustrated, the seal 5b is located closely adjacent the bearing assembly and disposed radially inwardly thereof. To this end, the pump unit housing lb is provided with a circumfer-entially extending flange portion 40b, the outer surface of which defines the seat for the inner ring 15b and which defines interiorly thereof, a pair of pockets separated by a thin web 4~b. The outer pocket 44b is outwardly flared to receive the central hub portion 46b of the drive member 3b which is pro~
vided with an opening within which the stub shaft 49b of the impeller is ~-mounted by a locking key 53b. The inner pocket 47b is outwardly flared in an opposite direction and mounts therein the seal 5b.
There is illustrated in Figure 4 a modified form of a pump unit ;
;:
.
~039573 constructed in accordance with the present invention. The pump unit is similar to the embodiment of Figure 3 and accordingly~ the basic elements thereof are designated with the same numera:Ls and a letter ~c~ postscript.
Thus, the pump unit includes a pump unit bearing housing lc, a bearing 2c, drive member 3c, an impeller 4c, and a sealing element Sc. In accordance with this embodiment of the invention, the seal Sc which circumscribes the shaft 49c of the impeller, is located close~Ly adjacent the bearing 2c, and is disposed in the radial center line C of the bearing. By this arrangement the seal is insensiti~e to any possible wobbling or warping and provides an optimum extended seal life potential. To accomodate the seal 5c in this location, there is provided an annular pocket defined in part by the inner circumferentially extending wall 41c of the Plange portion 40c, a radial shoulder 43c of the flange portion 40c, and a circumferential shoulder 45c aligned with the shoulder 43c at the juncture of the hub 47c of the impeller ;
4c and the stub shaft 49c. A snap ring 51c seats the seal 5c in the pocket.
As illustrated, the shaft 49c is suitably mounted in the opening in the drive member by a locking key 53c.
In the present instance, the axial length L of the pump unit assembly measured from the rotor 4c to the outer end of the drive member 3c and the pitch diameter Dm of the bearing are preferably of about the same order of magnitude. Additionally, the axial length L of the pump unit and the outer diameter D of the rotor 4 are preferably of the same order of magnitude. Further, the axial length L of the pump unit may be approximately equal to, or at most~ equal to the diameter Dr of the rotor 4. These re lationships provide the functional advantages set forth above in connection with the previously described embodiments.
The term "order of magnitude" as used herein is defined by the `~
following mathematical definition. Two quantities A and B are of the same "order of magnitude" if a ~3~ B~ A/ ~ . For example~ if B is 1 in., and A is ''' ' ' ' ~'..' . ' ' ` , . ' ' -' ' . ~ , .
IL~)3~3tS73 between 1.732 in. and 0.577 in., then A and B are of the same order of magnitude. Thus the axial length L of the pump unit and the pitch diameter D of the bearing are of about the same order of magnitude if D ~ ~ L
Dm~/ ~
The axial length L of the pump unit and the outer diameter of the impeller are of about the same order of magnitude if D ~ 3 ~ L ~ D ~ ~3.
_ 9 ~
.
The present invention relates to a pump unit for liquid cooled internal combustion engines, preferably for a motor car engine. The pump in accordance with the invention constitutes in mounted condition a unit in which the components preferably are undetachably united together.
The conventional cooling water pumps are so designed, that they consist of relatively large parts fastened together with screws and such pumps are relatively heavy and space consuming.
According to one aspect of the invention, a pump unit for liquid-cooled internal combustion engines comprises a bearing housing member, an aperture formed therein; a rotatable assembly including an impeller disposed adjacent one side of said housing member and rotatably supported by said housing member and a drive member for rotating said impeller and including a drive pully disposed adjacent the other side of said housing member, said , .~.
assembly including a connecting portion extending through said aperture and connecting said impeller to said drive member; bearing means supporting the drive member for rotation relative to the housing member; and a seal adapted to seal said aperture between said rotatable assembly and said housing member wherein the axial length L of the pump unit as measured from ~he impeller to the oppositely located end of the drive member and the pitch `
diameter Dm of the bearing means are related mathematically by the expres-sion L ~f~ ~ Dm ~ L/~
,: .
-1- ~
, . .
' . - ' ' ' ' ~39573 The advantages of fluid pumps in accordance with the present invention are the following: It is possible to select various materials for this shaftless type of pump. Suitable materials might be aluminum, plastics or pressed metal sheet. In selecting a suitable material, the pump will be cheap and light and has in relationship to the small weight, a good struc-tural strength. The good reliability in operation depends on the fact that there will be less unbalance and smaller masses in the pump components. An important feature of the pump unit of the present invention is its compact design. To this end, since there is no conventional shaft, the bearing of one embodiment of the pump unit is selected with greater pitch diameter and of about the same order of magnitude as the axial length of the pump unit measured from the impeller to the oppositely located end of the drive member.
Such a bearing, preferably of single row deep groove type, or in some cases of double row angular contact type, is simpler and axially more compact. i Additionally, the axial length of one embodiment of the pump unit measured ~ ~`
from the impeller to the outer end of drive member and the outer diameter of the impeller are of the same order of magnitude to provide a compact pump unit. Further, the axial length of the pump unit is of about the same or at most, equal to the diameter of the impeller. A further advantage is the possibility of getting a good sealing effect since the sealing diameter is ;~
very small. The pump unit is so designed that a good ventilating and drying of the bearing is obtained in front of, or behind the same, so that possible fluid particles will not get into contact with the bearing. Regarding an ~ ;
outer-ring-rotated bearing, it is possible to place the seal with its small diameter essentially :. - . : ,, . . .- - - :: ...
.: . ' . . ! . . .
- ' ' , .. .' ' ,' . " '. ~ ' ~ ~ ' ' ' ' ' ' ' .' ' ' ' ' ' ' ' ' ' ' , . ` ' `' ' ~ ' , ' . , ' ' ' , ,, . ~' ' ' " " ''' '. ' " ' ' ' ' , .. . .. . . ' ~L039573 `
in the radial center line of the bearing, whereby a considerable increase in the life of the seal is obtained.
The invention will now be described with reference to the accompanying drawings in which: Figure 1 shows an embodlment of the pump unit with a specially shaped inner-ring-rotated bearing;
Figure 2 shows a modification of the pump unit with an outer-ring-rotated bearing;
Figure 3 is a sectional view of still another embodiment of pump unit in accordance with the present invention; and Figure 4 is a sectional view of a modified form of the pump unit shown in Figure 3.
Referring now to the drawings and particularly to Figure 1 thereof, there is illustrated a pump unit constructed in accordance ~nth the present invention~ the main components of which include a pump unit bearing housing 1~ a bearing 2~ a drive member 3, a rotor or impeller 4~ and a sealing element 5. In the assembly illustrated, the pump unit housing 1 is detachably mounted by suitable means such as screws to the pump housing ~ to support the pump unit assembly in an opening in the pump housing, which may be a conventional volute casing. It is noted that the pump unit may be secured to the pump housing by other means; for example, by a press fit or be formed integrally therewith.
Figure 1 shows a cooling water pump in which the pump lmit bearing housing 1 consists of a relatively thin wall 6 of pressed sheet metal~ die~
casted aluminum or plastics which is fixed to a stronger housing portion 7 suitably of aluminum. In the portion 7, the outer ring 8 of the bearing 2 is fitted by shrinkage fit or otherwise. The inner and of the drive member 3 is of a stepped configuration to define the inner raceway 9 of the bearing and an axially extending seat 13 of smaller diameter than the raceway 9 for the seal S. As illustrated, a space or p~cket for the seal is provided between ~L039S73 the wall 6 of the pump unit housing 1 and the radial leg 30 of the drive member 3 connecting the raceway 9 and seal 13. The rotor 4 is mounted on the radial extension 32 depending from seat 13 by suitable means; for instance~
by welding or riveting. The inner raceway 9 is in the embodiment shown integrated with the drive member 3 of the pump unit, but the raceway might also be shaped in a separate inner ring fitted on the drive member 3 In the embodiment shown, the rolling bodies of the bearing consist of balls and the bearing is provided with a cage 10 of a suitable type. As shown in the figure, the inner ring will be rotated.
The pump unit is in this case driven by a belt from a suitable source of power. For this purpose the drive pulley part 11 of the drive member 3 is profiled on its outer surface as shown at 12. In the embodiment illustrated, the bearing is a single row deep groove ball bearing and the seal 5 is mounted radially inwardly of the pitch circle of the bearing.
Further, in accordance with the present invention, the axial length L of the pump unit measured from the rotor 4 to the outer end of the drive member 3 and the pitch diameter Dm of the bearing are preferably of the same order of magnitude. Additionally, the axial length L of the pump unit and the outer diameter D of the rotor 4 are preferably of the same order of magnitude.
~urther, the axial le~gth L of the pwmp unit may be approximately equal to, or at most, equal to the diameter D of the rotor 4. This arrangement pro-vides a very compact pump unit and facilitates the use of a comparatively simple type of bearing such as the single row deep groove ball bearing illustrated. Further, by this construction, the seal can be located in close proximity to the bearing and will be insensitive to any possible wobbling or warping, and thus have an extended life. Seal failure is one of the more common failures in the water pumps in the automotive field. Additionally, a compact pump unit design offers greater freedom in selection of materials so that the pump unit may be made very economically and of light weight .. . . . .
:' ~ '' ~ '' -' ., .
.
. . .:~ : -' ~
construction. ~o39~73 The various components of the pump unit provide a shaftless assembly wherein the various elements such as the bearing, d~ive member, impeller and pump unit housing preferably form an integral unit which is easily replace-able in the event of pump failure.
In new installations, the separable integral pump unit of the present invention is adapted for use with various pump housing designs thereby providing a standard unit which may be assembled to a plurality of different designed pump housing and therefore has a non-obsolescent characteristicO
Presently, as engine designs are changed, it often necessitates a correspond-ing design change in the entire water pump assembly.
In the pump unit housing 1 tnere is provided a number of large openings 14 intended for ventilating, drying and draining purposes. Through these openings there is obtained a very effective ventilating or draining in front of the bearing. Close to the drive side of the pump there can be applied a fan (not shown here). This can be designed in such a way that the fan is integrated with the drive member of the pump so that a combined fan and drive member is obtained. The fan can, of course, be a separate part fixed to the drive member. ~
In Figure 2 a modiication of the cooling water pump unit is shown --in which, unlike the above mentioned embodiment, the outer ring of the bearing rotates. The parts of the pump unit which are similar to the previously de- ;
scribed embodiment are referenced by the same numerals with the letter "a"
postscript. In this example a conventional bearing is used, for example, a single row deep groove ball bearing, the inner ring 15 of which is fitted on an annular part 16 of the pump unit bearing housing la. The outer ring 17 of the bearing is fitted into a bearing seat 18 in the drive member 3a. The outer surface of the drive pulley part of the drive member is profiled at 19 as in the first embodiment. The drive member is provided with a web portion : , . . .
~039~i73 20 which i5 fixed to a hub portion 21 of the impeller~ by~ for example~ weld-ing. The seal 5a is fitted to a suitable place on the portion 21 in connection with the inner part of the pump unit housing 1~. The seal can also be located in the radial center line of the bearing whereby angular warpings are elimin-ated. The drive member is also in this embodimant provided with large drain-ing/ventilating openings 22.
In the present instance, the axial length L of the pump unit assembly measured from the rotor 4a to the outer end of the drive member 3a, and the pitch diameter D of the bearing are preferably of the same order of magnitude.
10 Additionally, the axial length L of the pump unit and the outer diameter D i of the rotor 4 are preferably of the same order of magnitude. Further, the ~ ~-axial length L of the pump unit may be approximately equal to, or at most, equal to the diameter Dr of the rotor 4. These relationships provide the functional advantages set forth above in connection with the previously de-scribed embodiment. Further, as illustrated, the seal 5a is located closely adjacent the bearing assembly and disposed radially inwardly thereof. To this end, the housing la is provided with an annular recess defining two walls of a pocket for the seal at the juncture of the radial portion 24 of the housing la and the annular part 16. The other walls of the p~-cket, as illus- ;
trated, are defined by the rear face of the impeller and the hub portion 21.
Figure 3 shows another embodiment of pump unit in accordance with ~-the present invention. The elements of the pump unit similar to those of the previously described embodiment, are designated by the same numerals with the letter "b" postscript. Thus the pump unit comprises a pump unit housing lb adapted to be secured by suitable means to the main pump housing H , for example, in the manner described previously, a rotor or impeller 4b, one end of which is disposed interiorly of the pump housing H and is secured to a drive member 3b, which in the present instance has a sheave or pulley formed , ~ . , ~ .
,' ' : - - . .
~039573 integrally therewith for a belt connected to a suitable drive means to rotate the impeller. The drive member 3b mo~mts at its o~lter and remote from the pump unit housing lb, a fan wheel 29 connected at its hub portion 31 in a suitable manner, for example, by screws 34. The bearing 2b in the present instance, is illustrated as a single row deep groove ball bearing comprising an outer ring 17b fitted in the drive member 3b, an inner ring 15b fitted in the pump unit housing lb and a plurality of balls in the annular space between the rings. However, when a fan wheel 29 is provided, a double row angular contact ball bearing is preferred. The drive member is also provided, in -the present instance~ with draining/ventilati~g openings 22b.
In accordance with this embodiment, the axial length L of the pump unit measured from the rotor 4b to the outer end of the drive member 3b and the pitch diameter D of the bearing are preferably of the same order of magnitude. Additionally, the axial length L of the pump unit and the outer diameter D of the rotor 4 are preferably of the same order of magnitude.
Further, the axial length ~ of the pump unit may be approximately equal to~ -or at most, equal to the diameter D of the rotor 4. These relationships provide the functional advantages set forth above in connection with the previously described embodiments. Further as illustrated, the seal 5b is located closely adjacent the bearing assembly and disposed radially inwardly thereof. To this end, the pump unit housing lb is provided with a circumfer-entially extending flange portion 40b, the outer surface of which defines the seat for the inner ring 15b and which defines interiorly thereof, a pair of pockets separated by a thin web 4~b. The outer pocket 44b is outwardly flared to receive the central hub portion 46b of the drive member 3b which is pro~
vided with an opening within which the stub shaft 49b of the impeller is ~-mounted by a locking key 53b. The inner pocket 47b is outwardly flared in an opposite direction and mounts therein the seal 5b.
There is illustrated in Figure 4 a modified form of a pump unit ;
;:
.
~039573 constructed in accordance with the present invention. The pump unit is similar to the embodiment of Figure 3 and accordingly~ the basic elements thereof are designated with the same numera:Ls and a letter ~c~ postscript.
Thus, the pump unit includes a pump unit bearing housing lc, a bearing 2c, drive member 3c, an impeller 4c, and a sealing element Sc. In accordance with this embodiment of the invention, the seal Sc which circumscribes the shaft 49c of the impeller, is located close~Ly adjacent the bearing 2c, and is disposed in the radial center line C of the bearing. By this arrangement the seal is insensiti~e to any possible wobbling or warping and provides an optimum extended seal life potential. To accomodate the seal 5c in this location, there is provided an annular pocket defined in part by the inner circumferentially extending wall 41c of the Plange portion 40c, a radial shoulder 43c of the flange portion 40c, and a circumferential shoulder 45c aligned with the shoulder 43c at the juncture of the hub 47c of the impeller ;
4c and the stub shaft 49c. A snap ring 51c seats the seal 5c in the pocket.
As illustrated, the shaft 49c is suitably mounted in the opening in the drive member by a locking key 53c.
In the present instance, the axial length L of the pump unit assembly measured from the rotor 4c to the outer end of the drive member 3c and the pitch diameter Dm of the bearing are preferably of about the same order of magnitude. Additionally, the axial length L of the pump unit and the outer diameter D of the rotor 4 are preferably of the same order of magnitude. Further, the axial length L of the pump unit may be approximately equal to, or at most~ equal to the diameter Dr of the rotor 4. These re lationships provide the functional advantages set forth above in connection with the previously described embodiments.
The term "order of magnitude" as used herein is defined by the `~
following mathematical definition. Two quantities A and B are of the same "order of magnitude" if a ~3~ B~ A/ ~ . For example~ if B is 1 in., and A is ''' ' ' ' ~'..' . ' ' ` , . ' ' -' ' . ~ , .
IL~)3~3tS73 between 1.732 in. and 0.577 in., then A and B are of the same order of magnitude. Thus the axial length L of the pump unit and the pitch diameter D of the bearing are of about the same order of magnitude if D ~ ~ L
Dm~/ ~
The axial length L of the pump unit and the outer diameter of the impeller are of about the same order of magnitude if D ~ 3 ~ L ~ D ~ ~3.
_ 9 ~
.
Claims (7)
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A pump unit for a liquid-cooled internal combustion engine, such as a vehicle engine, said unit comprising a bearing housing member, an aper-ture formed therein; a rotatable assembly including an impeller disposed adjacent one side of said housing member and rotatably supported by said housing member and a drive member for rotating said impeller and including a drive pulley disposed adjacent the other side of said housing member, said assembly including a connecting portion extending through said aperture and connecting said impeller to said drive member; bearing means supporting the drive member for rotation relative to the housing member; and a seal adapted to seal said aperture between said rotatable assembly and said housing member, wherein the axial length L of the pump unit as measured from the impeller to the oppositely located end of the drive member and the pitch diameter D
of the bearing means are related mathematically by the expression .
of the bearing means are related mathematically by the expression .
2. A pump unit as claimed in claim 1 wherein a raceway for the bear-ing means is formed as part of said drive member and wherein said drive member is operatively connected by said connecting portion to said impeller.
3. A pump unit as claimed in claim 1 wherein said seal is an annular member of a smaller diameter than the pitch diameter of the bearing.
4. A pump unit as claimed in claim 1, 2 or 3 wherein said seal is located substantially in line with the radial center line of said bearing.
5. A pump unit as claimed in claim 1, 2 or 3 wherein said bearing means comprises a single row deep groove ball bearing.
6. A pump unit as claimed in claim 1, 2 or 3 including a plurality of draining and ventilating apertures closely adjacent said bearing means for draining coolent which may have passed said seal to a space between said seal and bearing means.
7. A pump unit according to claim 1, 2 or 3 wherein said impeller includes a central shaft connecting a hub portion of the drive member to said impeller.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US05/481,877 US3934966A (en) | 1971-11-11 | 1974-06-21 | Cooling water pump, preferably of motor car engines |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1039573A true CA1039573A (en) | 1978-10-03 |
Family
ID=23913747
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA229,540A Expired CA1039573A (en) | 1974-06-21 | 1975-06-17 | Cooling water pump, preferably for motor car engines |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1039573A (en) |
-
1975
- 1975-06-17 CA CA229,540A patent/CA1039573A/en not_active Expired
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