U.S. patent number 3,567,975 [Application Number 04/884,544] was granted by the patent office on 1971-03-02 for electric high-speed spindle with cooling means.
Invention is credited to Marvin L. Biesack, Donald W. Loomis.
United States Patent |
3,567,975 |
Biesack , et al. |
March 2, 1971 |
ELECTRIC HIGH-SPEED SPINDLE WITH COOLING MEANS
Abstract
A tubular housing piece and a tubular member telescoped within
the housing piece for defining separate liquid passageways.
Connectors are attached to the tubular assembly for conducting
liquid into and away from the assembly. An armature is rotatably
supported in the assembly by means of a bearing, and a bearing
support member is disposed adjacent the tubular member and its
liquid passageways so that the bearing support and the bearing
itself are cooled by liquid flowing through the passageways. The
tubular assembly is of one uniform diameter throughout the extent
of the liquid passageways, and the assembly has drilled holes in
one end, for providing the liquid inlet port and the liquid outlet
port in flow communication with the respective liquid
passageways.
Inventors: |
Biesack; Marvin L. (Racine,
WI), Loomis; Donald W. (Racine, WI) |
Family
ID: |
25384868 |
Appl.
No.: |
04/884,544 |
Filed: |
December 12, 1969 |
Current U.S.
Class: |
310/54;
310/57 |
Current CPC
Class: |
H02K
9/19 (20130101) |
Current International
Class: |
H02K
9/19 (20060101); H02k 009/19 () |
Field of
Search: |
;310/54--65 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Duggan; D. F.
Claims
We claim:
1. An electric high-speed spindle with cooling means, comprising a
tubular housing piece having an inner surface extending along the
longitudinal axis of said piece, an electric stator disposed inside
said housing piece, an electric armature rotatably mounted in said
stator and having an end extending beyond said stator and
presenting a front end of said armature, a work tool-holding member
connected to said armature front end and extending therebeyond for
releasably holding a work tool for rotation with said armature, a
bearing on said front end and on the opposite end of said armature
for rotatably supporting the latter, a bearing support member
interposed between said housing piece inner surface and said
bearing on said front end of said armature, a tubular member fluid
tightly telescoped within said tubular housing piece and extending
into overlying contact with said bearing support member, said
tubular member having a liquid inlet passageway spiraled therealong
and having a liquid outlet passageway spiraled therealong and with
said passageways extending along said tubular member to be in the
plane extending transverse to the longitudinal axis of said
armature and through said bearing support member for conducting
cooling liquid along said housing and adjacent said bearing support
member, said tubular housing piece and said tubular member fully
defining said liquid passageways and thereby being arranged to
fully contain the cooling liquid between said housing piece and
said tubular member for cooling said stator and said armature and
said bearing support member.
2. The subject matter of claim 1, wherein said tubular housing
piece and said tubular member are cylindrical throughout their
lengths and wherein said passageways are spiraled separate from but
adjacent each other and with a common crossover passageway in
liquid flow communication with both said spiraled passageways at
said location adjacent said bearing support member.
3. The subject matter of claim 1, wherein said bearings are
spaced-apart along said armature, said passageways extending along
said tubular member for a distance greater than the spacing between
said bearings for conducting liquid coolant to locations adjacent
said bearings.
4. The subject matter of claim 2, wherein said tubular housing
piece and said tubular member have both a fluid inlet port and a
fluid outlet port formed in both said tubular housing piece and
said tubular member and being drilled holes extending along the
mating telescoping surfaces thereof, and with respective ones of
said two ports being in fluid flow communication with respective
ones of said two passageways.
Description
This invention pertains to an electric high-speed spindle with
cooling means, The invention has particular application to spindles
used in the continuous production of items wherein there is a
problem of the heat generated by the spindle and its assembly. It
is the dissipation of this heat that is solved by this
invention.
BACKGROUND OF THE INVENTION
The prior art holds many examples of high-speed spindle structures
which are used in production of items and are used for drilling,
grinding, milling, and like functions. Further, the spindles known
heretofore are known to be either liquid or air cooled, and a
water-cooled spindle is commonly known. Still further, these
high-speed spindles are commonly powered by an electric motor, and
the operation of the motor, along with the operation of the
drilling or other like work tool, creates the problem of the tool
getting hot.
To air cool a high-speed spindle requires a substantial flow of
air, and this commonly results in noise produced by the flow of the
air. As such, an air-cooled spindle is not desirable. On the other
hand, liquid-cooled spindles have commonly required elaborate
liquid passageways and compartments, and they have also required
special dimensioning of the tool itself so that the tool can be of
a size adaptable to standard fixtures and the like in the use and
support of the tool. Therefore, the concern of one skilled in the
art of constructing high-speed spindles has been to provide a
water-cooled spindle which is of a limited outside dimension, say a
limited outer diameter, and which is sufficiently sturdy, even
though liquid passageways extend through the assembled spindle or
tool. The problem is not as simple as providing passageways in the
assembly, since the passageways must generally be to the outside of
the assembly and away from the inner electric motor, and the
provision and location of the passageways either weakens the
housing or it creates the probability of leaking the water coolant
to the electric motor or other working parts. In efforts to
overcome these problems, some prior spindle constructions
incorporate a coolant pocket, but this pocket creates the problem
of weakening the housing wall. Another problem is trying to seal
the water coolant so it stays in the pocket, and if O-rings are
used for sealing, they even weaken the wall more so. Where an
electric stator is involved, to try for a liquidtight fit directly
over the stator creates a problem of keeping liquid away from the
stator laminations. Also, to put a protective sleeve over the
laminations, then there is the problem of the limitation of the
overall dimension or diameter of the assembly. Still further, where
the prior art spindles utilize a coolant pocket, there is no
control of the path or flow of the coolant through the tool, since
the pocket simply collects the coolant rather than guides it
through the assembly tool.
It is a general object of this invention to provide a high-speed
spindle with cooling means which overcome the aforementioned
problems. Specifically, the present invention provides the tool
which has a cooling means presenting a definite and continuous path
from inlet to outlet and through the tool, and this results in
minimum of likelihood of liquid leakage and a maximum of cooling
efficiency. At the same time, the overall dimension of the tool is
retained within its limitations.
Still further, it is an object of this invention to provide a
high-speed spindle with cooling means and with bearings for the
rotational mounting of the spindle, and with the cooling means and
bearings being related so that the cooling means meets the
aforementioned requirements and overcomes the aforementioned
problems but also is efficient in cooling the spindle bearings.
Still further, the present invention overcomes the aforementioned
problems, and it accomplishes the aforementioned objects and it
does so with a tool which is of maximum efficiency and strength in
that the passageways provided for the flow of coolant do not weaken
the tool.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a longitudinal sectional view showing a preferred
embodiment of this invention;
FIG. 2 is a side view of a tubular member in FIG. 1, and showing
the member prior to its final form in the assembly and showing it
turned end-for-end from the position of FIG. 1;
FIG. 3 is a sectional view taken on the line 3-3 of FIG. 2.
FIG. 4 is a sectional view taken on the line 4-4 of FIG. 1.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT
FIG. 1 shows a tubular housing piece 10 enclosing an electric motor
having a stator 11 and an armature 12. The armature 12 includes the
axial-bearing pieces 13 and 14, and it also has the usual
rotational balance means. A collet 16 is attached to the projecting
end of the armature 12, in the usual and well-known manner, and the
collet releasably supports a work tool 17, which is indicated to be
a drill. A front ball bearing 18 and a rear ball bearing 19 are
shown in abutment with the armature members 13 and 14,
respectively, and the ball bearings 18 and 19 are supported in ball
bearing support members 21 and 22, respectively. Further, the
support member 21 serves as a housing insert and lends structural
support to the tubular housing piece 10, and the member 21 is
suitably affixed to the end of the housing piece 10. A bearing
retainer ring 23 is threaded or otherwise secured to the support
piece 21 to abut the bearing 18, and a bearing retainer washer 24
abuts the bearing 19 and is secured to the armature 12 through the
screw 26. Thus the armature 12 is axially located and rotatably
mounted in the assembly.
A seal nut 27 and seal 28 are also located in the front end of the
tool, and they serve to keep the tool clear of dirt and the
like.
The rear end of the tool has an electric receptacle 29 extending
through the housing rear end insert or cover member 31 and electric
wires 32 extend from the receptacle and to the stator 11, as shown.
Also, liquid connectors 33 and 34 are shown threaded into the end
piece 31, and it will be understood that they conduct liquid
coolant, such as water, into and out of the assembly shown.
A tubular member 36 extends for substantially the length of the
housing tubular piece 10, but it ends in the abutment of the
housing shoulder 37. The tubular housing piece 10 and the tubular
member 36 are of the same cross-sectional shape to the extent that
they are telescoped together, and they are preferably cylindrical
in their cross-sectional shapes. Thus, the housing piece 10 has an
inner surface 38 and the tubular member 36 has an outer surface 39,
and these surfaces are in liquidtight contact throughout the length
of the tubular member 36, except as hereinafter described.
The outer surface 39 of the tubular member 36 has two sets of
liquid passageways, 41 and 42. These passageways 41 and 42 are
spirally shaped grooves extending around the tubular piece 36 and
for substantially the whole length of the piece 36, as best seen in
FIG. 2 which shows the passageway 41 to have an end 43, while
passageway 42 has an end 44, and these ends are also shown in FIG.
3. For the purpose of most complete description of the invention,
FIGS. 2 and 3 show the tubular piece 36 prior to its final form in
the assembly in FIG. 1. That is, in FIG. 1, the telescoped member
10 and piece 36 have drilled openings 46 and 47 cutting into and
extending along the mating abutting surfaces 38 and 39 of the
member 10 and piece 36, respectively. However, FIGS. 2 and 3 show
the piece 36 prior to assembly and therefore prior to the provision
of the drilled holes 46 and 47, which serve as the liquid inlet and
liquid outlet ports, respectively. That is, the assembly of pieces
10 and 36 is made and they are then prepared with the drilled holes
46 and 47, so that the holes are short and properly located, and
they do not weaken the structure to any significant degree. Also,
the holes 46 and 47 are in separate flow communication with the
liquid passageways 41 and 42, and the passageways 41 and 42 extend
along and are defined by the grooves in the member 36, and they are
liquidtight from each other by virtue of the telescoping with the
tubular housing piece 10, except for a crossover portion designated
48 in FIG. 2. That is, liquid coolant, such as water, may enter the
connection 33 and the inlet port 46 and the inlet liquid passageway
41, and this passageways extends to the designation 41 on the right
end in FIG. 2 and is completely separate from the passageway 42
throughout the extent along the tubular member 36, until the
passageway 41 reaches the crossover or common passageway 48.
Similarly, liquid passageway 42 extends along the length of the
member 36 and is in flow communication with the crossover pocket or
portion 48. Therefore, liquid flowing in the passageway 41 will be
in flow communication with the passageway 42 when the liquid
reaches the crossover portion 48, and it will then be in a return
flow pattern back to the opening 44 on the passageway 42. The
liquid coolant will then enter the outlet port 47, and from there
it will flow into the outlet connection 34, all as desired.
To further show the arrangement of the ports and openings and
passageways, FIG. 4 shows the inlet port 46 and the outlet port 47
formed at the juncture of the housing piece 10 and tubular member
36. One upper O-ring 49 and one lower O-ring 51 are disposed
intermediate the ends of the telescoped assembly of piece 10 and
member 36 and against the housing end member 31, as shown in FIGS.
1 and 4. These O-rings 49 and 51 serve to liquid seal the fluid
flow paths described, but they do not weaken the structure since
they are not located at any point where weakening could occur and
where strength is more important, such as at the front end of the
housing and adjacent the bearing support member 41, for instance.
Instead, at that front end, the tubular piece 36 has its continuous
annular surface 52 in liquidtight contact with the inner
circumferential surface 38 of the housing piece 10. FIG. 4 further
shows the circular mating juncture designated 53 and being the
location of the mating surfaces 38 and 39.
It will now be seen and understood that the liquid-flow paths
described extend beyond the spacing between the bearings 18 and 19,
and, more specifically, the liquid passageways 41 and 42 extend
through the ends of the tubular member 36, which ends are in direct
contact with the bearing support members 21 and 22. Therefore, the
bearings 18 and 19 are also cooled by the arrangement described.
Further, there are no sump pockets or other cavities in the
assembly for the flow or accumulation of the coolant, so the
assembly is not weakened but is a sturdy structure. Likewise, the
assembly is limited in overall diameter of say less than the
standard 21/2 inches across the housing piece 10. Such limited
diameter permits the standardized support in mounting of the
assemble tool in its work installations. Also, the spiraled groves
41 and 42 are arranged with maximum flow capacity in their
cross-sectional areas, and the intervening lands 54 are substantial
for structural support, so the passageways are provided but the
tool is not structurally weakened, and this is in contrast to
cooling passageways which extend only longitudinally of the tool,
rather than being spiraled therearound and having the full flow and
guided flow throughout the length of the tool as described
herein.
* * * * *