U.S. patent number 3,582,159 [Application Number 05/036,345] was granted by the patent office on 1971-06-01 for machine bearing.
This patent grant is currently assigned to The Heald Machine Company. Invention is credited to Herbert R. Uhtenwoldt.
United States Patent |
3,582,159 |
Uhtenwoldt |
June 1, 1971 |
MACHINE BEARING
Abstract
This invention relates to a machine bearing and, more
particularly, to a machine construction having hydrostatic
ways.
Inventors: |
Uhtenwoldt; Herbert R.
(Worcester, MA) |
Assignee: |
The Heald Machine Company
(Worcester, MA)
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Family
ID: |
21888089 |
Appl.
No.: |
05/036,345 |
Filed: |
May 11, 1970 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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729690 |
May 16, 1968 |
3512848 |
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Current U.S.
Class: |
384/12;
384/100 |
Current CPC
Class: |
F16C
29/025 (20130101); F16C 32/06 (20130101) |
Current International
Class: |
F16C
29/02 (20060101); F16C 29/00 (20060101); F16c
017/16 () |
Field of
Search: |
;308/5,9,122 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Kaufman; Milton
Assistant Examiner: Lazarus; R.
Parent Case Text
CROSS-REFERENCE TO RELATED APPLICATION
This application is a division of Pat. application Ser. No.
729,690, filed May 16, 1968, now U.S. Pat. No. 3,512,848.
Claims
The invention having been thus described, what I claim as new and
desired to secure by Letters Patent is:
1. A machine bearing, comprising
a. a first element having a pair of oppositely directed
surfaces,
b. a second element having a surface lying parallel to and slightly
spaced from each of the said pair of surfaces to define a gap
associated with each of the said pair of surfaces, a passage
opening into each gap, and
c. means regulating the flow of pressure fluid to each passage to
maintain the thickness of the two gaps at a predetermined value,
the said means including a secondary passage opening at one end
into each gap adjacent the first-mentioned passage and connected at
its other end to a shallow pocket located in the other gap.
2. A machine bearing as recited in claim 1, wherein each said
secondary passage includes a groove which is concentric with the
opening of the first-mentioned passage onto its surface.
Description
BACKGROUND OF THE INVENTION
In the design of machine tools and the like, it is common practice
to use hydrostatic bearings between the relatively movable
elements. Such bearings have the advantage of no moving parts and
low friction. However, they have had the disadvantage that, when
the load on the bearing changes, the distance between the bearing
surfaces changes. In a machine tool, this can mean a substantial
change in the geometric relationship between the tool and the
workpiece and, therefore, an inaccuracy in the finished surface.
Attempts in the past to correct this deficiency in hydrostatic
bearings have been complicated and expensive and have been unstable
and have been slow in response to load changes. These and other
difficulties experienced with the prior art devices have been
obviated in a novel manner by the present invention.
It is, therefore, an outstanding object of the invention to provide
a machine bearing having a high spring constant.
Another object of this invention is the provision of a machine
bearing of the hydrostatic type, wherein a change in load results
in relatively little change in the distance between the
surfaces.
A further object of the present invention is the provision of a
machine bearing having a self-compensating hydrostatic system.
It is another object of the instant invention to provide a machine
bearing of the hydrostatic type, wherein the construction is simple
and inexpensive and which is capable of a long life of useful
service with a minimum of maintenance.
A still further object of the invention is the provision of a
hydrostatic bearing system whose operation is extremely stable and,
yet, responds quickly to correct for changes in load.
It is a further object of the invention to provide a hydrostatic
bearing system in which a standard design of adjustable restrictor
can be used where different numbers of pockets are served from a
main passage.
Another object of the invention is to provide a hydrostatic bearing
system in which the necessary accuracy of manufacture is reduced;
in a conventional fixed resistor hydrostatic bearing the stiffness
(k=1.5 w/h) is proportional to the bearing preload in inversely
proportional to the clearance; with the present invention the
clearance, h.sub.B, can be made five times as large and still
provide greater stiffness than a conventional hydrostatic
bearing.
A still further object of the invention is the provision of a
hydrostatic bearing system, including a load-sensitive variable
restrictor which is simple to manufacture and is an integral part
of the system, so that the distance between the pockets and the
restrictor is small and the fluid volume effected is small, thus
shortening response time and increasing the stability of
operation.
With these and other objects in view, as will be apparent to those
skilled in the art, the invention resides in the combination of
parts set forth in the specification and covered by the claims
appended hereto.
SUMMARY OF THE INVENTION
In general, the invention consists of a machine bearing having a
first element with a pair of oppositely directed surfaces, having a
second element with a surface lying parallel to and slightly spaced
from each of the said pair of surfaces to define a gap associated
with each of the said pair of surfaces, having a passage opening
into each gap, and having means for regulating the flow of pressure
fluid to each passage to maintain the thickness of the two gaps at
a predetermined value.
BRIEF DESCRIPTION OF THE DRAWINGS
The character of the invention, however, may be best understood by
reference to one of its structural forms, as illustrated by the
accompanying drawings, in which:
FIG. 1 is a transverse sectional view of a machine bearing
incorporating the principles of the present invention,
FIG. 2 is an end view of the bearing with portions broken away,
FIG. 3 is a sectional view of the invention taken on the line
III-III of FIG. 2,
FIG. 4 is a perspective view of the bearing,
FIG. 5 is a vertical sectional view of the bearing taken on the
line V-V of FIG. 2,
FIG. 6 is a sectional view of a modified form of the bearing,
FIG. 7 is a sectional view taken on the line VII-VII of FIG. 6,
FIG. 8 is a modified form of the restrictor,
FIG. 9 is a transverse sectional view of another form of the
bearing,
FIG. 10 is a sectional view taken on the line X-X of FIG. 9,
FIG. 11 is a sectional view of a further modification of the
bearing,
FIG. 11 is a sectional view of a further modification of the
bearing,
FIGS. 12 and 13 show other external loading conditions of the
bearing shown in FIG. 11,
FIG. 14 is a vertical sectional view of another modification of the
bearing, and
FIG. 15 is a view of the bearing taken on the line XV-XV of FIG.
14.
DESCRIPTION OF THE PREFERRED EMBODIMENT
Referring first to FIG. 1, wherein are best shown the general
features of the invention, the machine bearing, indicated generally
by the reference numeral 10, is shown as forming part of a machine
tool 11 having a table 12 and a base 13. Another similar bearing 14
is incorporated in the machine tool, the two bearings 10 and 14 is
incorporated in the machine tool, the two bearings 10 and 14
supporting the table 12 on the base 13 for frictionless relative
sliding motion therebetween. A linear actuator, such as a hydraulic
cylinder 15, connects the table and base to produce such motion.
Attached to the table 12 is a way 16 having four surfaces 17, 18,
19, and 21, these surfaces lying parallel to and slightly spaced
from surfaces 22, 23, 24, and 25, respectively, of the base 13. An
inlet port 26 is formed in the table for connection to a source of
pressure fluid (not shown). This port is connected by passages to a
main passage 27 extending longitudinally into the way 16. Extending
radially from the passage 27 to the surfaces 17, 18, 19, and 21,
respectively, are passages 28, 29, 31, and 32, each passage opening
onto a shallow pocket formed on its outlet surface.
As is evident in FIG. 2, the base 13 is provided with a separate
rail 33 and is formed with an inverted L-shape to provide the two
base surfaces 22 and 25. A special post 34 extends upwardly from
the lower part of the base into a downwardly directed bore 35 in
the rail, the bore diameter being much greater than that of the
post. A bolt 36 and a set screw 37 serve to connect the post and
rail while allowing adjustment. A regulating means 38 is bolted to
the end face of the way 16 and extends into the main passage 27 to
a point well past the passages 31 and 32.
The perspective view of FIG. 4 shows the interrelationship of the
parts particularly well. The upper part of the table 12 is removed
and the location of the hydrostatic pockets is clearly
disclosed.
FIG. 5 shows the details of the regulating means 38. A flat
plate-type restrictor 39 is supported by a reed 31. This reed (in
the form of a cantilever spring) allows the clearance of the
restrictor to vary in accordance with the pressure in the
hydrostatic pockets. When a pocket pressure increases, because of
higher load and because of deflection which reduces the pressure
around the sill area of the pocket, it will react against the
restrictor 39 and bend its supporting spring 41. This movement
serves to open the restrictor clearance, h.sub.R, which reduces the
pressure drop (in a cubic relationship) over this input resistance,
thus providing more pressure in the pocket. This increase in
pressure in the pocket serves to support the increased load and to
increase the flow through the pocket in such a manner that the
clearance or sill gap, h.sub.B, remains virtually constant or, in
any case, changes to a lesser degree than if clearance of the input
resistance had remained constant.
With the present bearing design, an endeavor has been made to
obtain very great stiffness, which means that the bearing clearance
or gap, h.sub.B, must remain constant with changing load. This
meant that, in addition to an increase in pocket pressure to
support the additional load, the flow rate, Q, from the pocket
through the gap to fluid collection points has to increase
proportionately. In other words:
Q =L.times.(h.sub.B).sup.3 .times.P.sub.P /12 .times.b
where: Q = fluid flow rate, in..sup.3 /sec.
L = sill length
h.sub.B = bearing clearance or gap
P.sub.p = pocket pressure
.mu. = dynamic viscosity of the fluid
b = sill width
It is clear from this equation that an input restrictor is required
through which the flow rate increases linearly with the pocket
pressure. It can be shown by mathematical analysis and proven by
test that when the spring constant, K.sub.c, of the reed 41 is
equal to 1.5 A.sub.R.times. P.sub.s /h.sub.R (where A.sub.R is the
effective area against which pressure impinges to deflect
restrictor and P.sub.s is the supply pressure), the rigidity of the
hydrostatic bearing is infinite with a load change up to 40
percent. If the spring constant is made larger, the stiffness of
the bearing will decrease. With an infinite spring constant for the
reed, the rigidity of the bearing will, of course, be that of a
capillary (fixed restrictor) bearing. With a weaker reed spring
constant, the hydrostatic bearing would have "negative" stiffness.
This negative stiffness could be a desirable feature for certain
applications and can be used to compensate for mechanical
deflection, i.e., elastic deformation of machine elements. For
instance, in an internal grinder, a negative stiffness in the
hydrostatic bearing of a slide way could be designed to compensate
for the deflection of the spindle and the like, such that, when the
force between the work and the wheel is reduced, the bearing would
back off, thus releasing the various elastic deflections in the
system and bringing about a quick "sparkout." The value of negative
rigidity (and, thus, the amount of backoff) could be adjusted by
moving the compensator axially (changing b.sub.R A.sub.R) or by
changing the supply pressure P.sub.s. The resistance to flow of a
hydrostatic pocket is a function of the sill width divided by the
sill length and the third power of the gap; that is to say:
R.sub.p =b/L h.sub.B .sup.3
To obtain the optimum rigidity, the pressure drop over the input
resistance, R.sub.c, should be equal to the pressure drop over the
output resistance, R.sub.p of the pocket. With a sill width of
one-fourth inch and a usual length ratio of L.sub.P /L.sub.R = 8,
the clearance of the compensator restrictor would be twice that of
the hydrostatic bearing, which means that the manufacturing
tolerances are easy to meet.
FIGS. 6, 7, and 8 show a variation of the load-variable restrictor
in which a restrictor 42 is mounted in a main passage 43 in a way
44. Two oppositely directed passages 45 and 46 lead from the main
passage to hydrostatic pockets 47 and 48, respectively. A tube 49
fits slidably in its inner portion in the bore or main passage 43,
has its diameter reduced in an outer free portion adjacent the
passages 45 and 46, and has its sides cut away in the same vicinity
to define two reeds 51 and 52. As is evident in FIG. 7, the reeds
are free of one another and move independently toward and away from
their respective radial passages. A plug 53 is threaded into the
inner portion of the tube 49 and is accessible through an input
pressure port 54 to adjust it axially to change the spring constant
of the reeds.
FIG. 8 shows a square or flat plate restrictor design which is used
in a bearing system. If loaded, it will not effect the input
resistances to ports 73a and 75a, but only the resistance values of
ports 72a and 74a, as is required due to a load change. This square
restrictor head gives better performance but is costlier to
manufacture than the round type shown in other views. To circumvent
the difficulties of manufacturing the square hole, the port 74a in
FIG. 8 is created by inserting a bushing whose end face acts as the
restrictor against the square pintle 78a.
In FIGS. 9 and 10 are shown a circular hydrostatic bearing having a
pocket extending completely around a spindle 55. A main passage 56
extends axially through the spindle and receives fluid pressure at
one end. A restrictor 57 is mounted in the other end. A plurality
of radial secondary passages 58 extend from the main passage to the
circumferential gap or pocket 59a. The restrictor 57 is provided
with a cylindrical head 59 having a conical portion 61; by moving
the head axially along the main passage, it is possible to adjust
the input resistance associated with all the secondary passages
58.
FIGS. 11, 12, and 13 show another variation of the invention
wherein a way 62 is provided with four surfaces 63, 64, 65, and 66
having hydrostatic pockets 67, 68, 69, and 71, respectively, which
are connected by passages 72, 73, 74, and 75 to a main passage 76.
The main passage is connected at one end to a fluid pressure source
and has a restrictor head 78 mounted on reed 77 in the other end.
The head 78 is adjusted axially to obtain the desired pressure drop
(as shown in FIG. 12), such that under initial conditions the head
78 is in the center of the bore 76 and the input resistances of the
various secondary passages are equal. From this center initial
position shown in FIG. 12, the restrictor head 78 will deflect off
center in the direction opposing the external load vector as shown
in FIG. 11 and 13. Instead of the hydrostatic slide deflecting in
the direction of the load as in a conventional hydrostatic bearing,
rather the spring supported restrictor head deflects in the
direction of the load, thus changing flow and pressure to the
hydrostatic bearing pads to minimize or even eliminate any
deflection of the slide. The eccentric positioning of the head
shown in FIG. 11 tends to increase the input resistance of the
secondary passages 72 and 75 and to reduce the input resistance of
the passages 73 and 74. The eccentric position shown in FIG. 13
increases greatly the input resistance to the passage 72, decreases
greatly the resistance to the passage 74, but maintains equal input
resistance to the passages 73 and 75 even though they are lower in
value than in the balanced situation shown in FIG. 12.
The machine bearing shown in FIGS. 14 and 15 is self-compensating.
A table way 79 has upper and lower flat surfaces 81 and 82 which
lie opposite and slightly spaced from similar flat surfaces 83 and
84 formed on a base 85. A main passage 86 enters the end of the way
and is connected to a source of fluid pressure. The main passage is
connected by a passage 87 to the upper surface 81, while it is
connected by a passage 88 to the lower surface 82. Concentric with
the opening of the passage 87 onto the surface 81 is a groove 89
whose inner portion is connected by a passage 91 to a large shallow
hydrostatic pocket 92 formed on the underside or lower surface 82
of the way. Similarly, a concentric groove 93 is formed around the
opening of the passage 88 on the lower surface 82; this groove is
operatively connected by a passage 94 to a large shallow
hydrostatic pocket 95 formed on the upper surface 81 of the way.
The operation of this bearing can be readily understood in view of
the above description. First of all, in the case of the prior art
hydrostatic bearing, a fixed resistance is connected into the fluid
line leading to the hydrostatic pocket; for this purpose, a
capillary coil is used of such a size that the amount of fluid
flowing through it is equal to the amount of fluid flowing through
the outgoing resistance. This outgoing resistance is the resistance
represented by the surfaces of the gap surrounding the pocket.
Furthermore, the input resistance is usually selected to cause the
pressure in the hydrostatic pocket to be equal to roughly one-half
the supply pressure. The hydrostatic pocket is, of course, sized so
that its effective force (pocket area, A.sub.p, multiplied by the
pocket pressure, P.sub.p, plus the area of land surrounding the
pocket multiplied by one-half the pocket pressure) is equal to the
effective load, W. As the load, W, is increased, the unit tries to
deflect downwardly. When this happens, the outgoing resistance is
increased and the flow of fluid through this resistance decreases;
the pressure in the pocket then increases. When the effective
pocket force is equal to the new total applied load, the system is
again balanced. However, the gap (or fluid film thickness) between
the loaded element and the supporting element is now less than when
supporting the old lesser load. The position of the loaded element
has now changed to a lower position. If the loaded element is part
of a machine tool, an error has now been introduced.
With the present invention, the incoming resistance is variable in
such a way as to maintain the gap (and, therefore, the position of
the loaded element) the same, despite changes in load. Now, in the
version of the invention shown in FIGS. 14 and 15, the incoming
resistance is defined by the clearance between the flat surface of
the base 13 (the supporting element) and the annular ring between
the passage and the groove; in the illustration, it can be seen
that this annular ring is the end of a tube that has been pressed
into a bore in the way. The amplitude of this resistance is a
function of the face width of this annular ring and it is sized to
equal the pressure drop past the outgoing resistance (main pocket
plus receiver pocket) and to cause the pocket pressure to be
one-half the supply pressure. For this system, a preload force is
generated by the upper hydrostatic pocket. The lower pocket must
then be sized so that its effective force will equal the total of
this preload force and the load. In operation, the fluid flows into
the supply pockets through the tubing connection at the input port
86 at the end of the way 79. It then flows across the incoming
resistance into a receiver pocket. By means of the interdrilling
(passages 91 and 94), the fluid flows from the receiver pocket to
the main pocket (92 or 95) on the opposite side of the way 79. When
an additional load is applied (in the direction of the arrow), the
way 79 tries to deflect in the direction of the load. In so doing,
the incoming resistance on the upper side tends to decrease and the
resistance around its main pocket (on the bottom side) tends to
increase. This allows more fluid to flow through the upper incoming
resistor and less through the sill of the main pocket 92. This
causes the pressure in the main pocket 92 to increase faster than
if the incoming resistance were fixed. A similar situation exists
for the upper main pocket 95, except that its pressure is caused to
decrease. This system has many advantages over the prior art,
including the following:
a. Capillary coils and their associated connecting tubing are no
longer needed.
b. No space is needed to house capillary coils.
c. There is less contained volume of fluid between the incoming
resistance and the hydrostatic pocket, which means that the system
will have a smaller time constant and will be more responsive to
changes in load.
d. Since the incoming and the outgoing resistances vary with the
load, the pocket pressure will change more for a given deflection
of the way, which has the effect of causing the system to have
greater stiffness.
e. The stiffness of the way is a function of the preload force and
the gap; the stiffness can be increased because the upper main
pockets force the way down in the direction of the load. This
increases the total preload and keeps the gap constant, therefore,
increasing the stiffness.
f. When used with ways having low mass, the preload effect causes
the way to appear to weight more, thus making the way system to
seem stiffer.
It is obvious that minor changes may be made in the form and
construction of the invention without departing from the material
spirit thereof. It is not, however, desired to confine the
invention to the exact form herein shown and described, but it is
desired to include all such as properly come within the scope
claimed.
* * * * *