Information
-
Patent Grant
-
6345969
-
Patent Number
6,345,969
-
Date Filed
Wednesday, June 28, 200024 years ago
-
Date Issued
Tuesday, February 12, 200222 years ago
-
Inventors
-
Original Assignees
-
Examiners
- Denion; Thomas
- Trieu; Theresa
Agents
-
CPC
-
US Classifications
Field of Search
-
International Classifications
-
Abstract
A hydraulic gerotor motor utilizing the holes surrounding the main assembly bolts together with interconnecting radially extending passages so as to allow for the transfer of fluid axially through the device from a single fluid input hole to an area 360° surrounding a valve.
Description
FIELD TO WHICH THE INVENTION RELATES
This invention relates to a series of plates for a hydraulic motor which improve the volumetric efficiency of the motor.
BACKGROUND OF THE INVENTION
Hydraulic motors have been utilized to provide power to a negative mechanism (such as a motor for a drivewheel or winch) or to derive power from a positive mechanism (such as a fluid pump driven by a gasoline motor). In some instances, the device is also utilized for a secondary purpose such as controlling the speed of rotation of itself or an auxiliary member.
Most hydraulic devices are relatively large in diameter for a given volumetric efficiency. The reason for this is the constraints in the cross-sections of the fluid passages which are necessary in the body of such hydraulic device. Examples of devices with limited cross-sectional passages include the Ross Gear MF-MG series which include a separate series of set diameter holes interconnected in alternate plates by set diagonal passages to provide for a fluid path axially through the manifold between (and separately from) the main bolts. In this Ross device both the holes and lateral slots have limited cross-sections, thus limiting the amount of fluid which is able to pass axially through the manifold. Some devices partially neighbor a bolt—examples include the bi-directional valving passage in U.S. Pat. No. 5,173,043, Reduced Size Hydraulic Motor, and the uni-directional passages in U.S. Pat. No. 3,452,680, Hydraulic Motor Pump Assembly and U.S. Pat. No. 3,452,543, Hydrostatic Device. However this usage is limited to a single location surround (U.S. Pat. No. 5,173,043) or a symmetrical Passageway (U.S. Pat. Nos. 3,452,680, 3,452,543).
SUMMARY OF THE INVENTION
It is an object of this invention to increase the volumetric efficiency of a given diameter hydraulic motor.
It is an object of this invention to utilize areas neighboring bolts to provide fluid passages for the device.
It is an object of this invention to utilize the inside surface of bolts to physically locate parts in respect to each other.
It is a further object of this invention to reduce the cost of motors.
It is another object of this invention to lower the heat generated by hydraulic motors.
It is yet another object of this invention to facilitate the manufacturer of hydraulic motors.
It is still a further object of this invention to lower the tolerances in hydraulic motors.
Other objects of the invention and a more complete understanding of the invention may be had referring to the drawings in which:
DESCRIPTION OF THE DRAWINGS
FIG. 1
is a cross-sectional side view of a hydraulic motor incorporating the invention;
FIG. 2
is a side view of the manifold of the motor of
FIG. 1
;
FIG. 3
is an end view of the manifold of
FIG. 2
, taken along lines
3
—
3
in
FIG. 1
which side would ordinarily face the rotor of the hydraulic device;
FIG. 4
is an end view of the manifold of
FIG. 2
, taken along lines
4
—
4
in
FIG. 1
which side would ordinarily face the valve of the hydraulic motor;
FIG. 5
is a cross-sectional view of the wear plate of
FIG. 1
taken generally from lines
5
—
5
therein;
FIG. 6
is an end view of the bearing port section of
FIG. 1
taken generally from lines
6
—
6
therein;
FIG. 7
is an end view of the end cover taken from lines
7
—
7
in FIG.
1
.
FIG. 8-12
are sequential cross-sectional views of the various plates utilized to make up the manifold of
FIG. 2
;
FIG. 13
is an enlarged view of a part of
FIG. 4
detailing the areas providing fluid passages surrounding the bolts holding the device together; and
FIG. 14-17
are modified cross-sectional views of
FIGS. 8
,
9
,
11
, and
12
showing optional modification to provide for 360° transfer of fluid within the manifold.
DETAILED DESCRIPTION OF THE INVENTION
This invention relates to an improved pressure device with increased volumetric efficiency. The invention will be described in its preferred embodiment of a gerotor motor having an orbiting valve separate from the rotor.
This invention relates to an improved fluid passageway for a gerotor pump/motor
10
(a pump supplies fluidic power on rotation of a shaft while a motor supplies rotation of a shaft on application of fluid pressure—a single device can do both).
The gerotor motor
10
has a housing
11
including a bearing port section
20
, a gerotor structure
30
, a manifold
40
and an end plate
70
.
The housing
11
includes all of the parts of the gerotor motor
10
. Its purpose is to locate the various fixed and movable parts in their operative positions in respect to each other. It also provides for a method of locating the gerotor motor onto an external structure as well as providing for the necessary fluidic interconnections thereto.
The bearing port section
20
rotatively supports the driveshaft
21
in respect to the housing in addition to providing for a specific location for the two fluid ports
27
,
28
for the device. The ports could be located otherwise if desired (including one or both in the end plate
70
) as long as the ports communicate with the valve as hereinafter set forth.
The driveshaft itself
21
is a generally cylindrical shaft supported by two needle bearings
22
to the surrounding section
20
. A main seal
23
retains the hydraulic fluid within the housing
11
while a thrust bearing
24
against a shoulder of the driveshaft prevents the extrusion of the driveshaft upon the pressurization of the central cavity
26
containing the driveshaft. If the device is a closed center device such as shown in U.S. Pat. No. 5,135,269, has a case drain such as shown in U.S. Pat. No. 5,165,880 (both incorporated by reference) or otherwise has an unpressurized case the main seal requirements are reduced.
The ports
27
,
28
serve to interconnect the gerotor motor to a source of pressure and return via hydraulic lines (not shown). The use of the ports on the bearing/port section
20
allow for the maintenance of the remainder of the gerotor motor without the removal of the entire unit from its associated component (such as a frame for a wheel drive or winch drive). The location also serves to physically protect such fluid interconnections from mechanical damage by locating them neighboring structural members of the associated device.
In the embodiment disclosed, one port
27
is interconnected to the central cavity
26
of the bearing port section
20
while the other port
28
is interconnected to a hole
25
which extends to the rear face of such section
20
(purpose later set forth—FIG.
6
. These two connections ultimately operatively connect respectively to the operative opposing sides of the valve.). Enlarged holes
29
surround each tapped bolt hole in the rear surface of the bearing section
20
. These holes
29
provide for an increased area for fluid passage about the bolts
90
. In addition the section
20
includes part of the 360° fluid connection in the remainder of the device.
In the embodiment disclosed, the housing
11
is 3.4″ long with a diameter of approximately 3.62″ with the seven tapped bolt holes some 0.272″ in diameter equally spaced and located on a 2.8″ bolt circle. The bolt holes themselves are approximately 1″ deep and tapped to engage the threaded end of the bolts ({fraction (5/16)}″×24 UNF thread). The threaded engagement between the bolts
90
and bearing/port section
20
retain the bolts in position with the housing
11
. The enlarged holes
29
in the housing
11
surrounding each bolt hole are ½″ diameter located on a 2.63″ bolt circle with their axis offset from the seven bolt holes. The hole
25
extending to the port
28
is approximately {fraction (5/16)}″ diameter 0.313 deep positioned approximately 60° from the lateral axis on an approximately 1.35 radius. The groove
19
is milled 0.20 deep between at least two holes
29
. Multiple segmented grooves or a continuous 360° groove could be utilized if desired.
The gerotor structure
30
is the main power development element for the gerotor motor
10
. The particular gerotor structure
30
disclosed includes an orbiting rotor
31
located within a fixed stator
32
as is known in the art. The internal teeth of the stator
32
are formed by cylinders
33
captured in semi-circular cavities within such stator
32
. This allows for the efficient manufacture of the stator as well as slightly increasing the mechanical efficiency of the gerotor structure. A wobblestick
34
serves to drivingly interconnect the rotor
31
to the driveshaft
21
by a toothed interconnection with each in a conventional manner.
The particular stator has seven holes in it approximately 0.38″ in diameter on a 2.845″ diameter bolt circle. These holes cooperate with the holes
29
in the port section
20
in order to feed fluid to the passages
43
in the later described manifold
40
. The inside extent of these holes
152
cooperate with the inside surface of the bolts
90
to physically locate the stator
32
in position in respect to the housing
11
. This is preferred in that the bolt/stator contact is in compression and/or shear in close proximity to the location of force generation (the pressure cells). This avoids the flexing unequal elongation that is present in a device having contact outside of the bolts 180° from the location of force contact. The rotor/stator side clearance is on the order of 0.001″.
A wear plate
35
on one side of the gerotor structure
30
and a manifold
40
on the other side of the gerotor structure serve to seal the two axial ends of the gerotor structure, thus to finish the definition of the expanding and contracting gerotor chambers located between the rotor and the stator. They also serve to distribute fluid to and from the gerotor structure.
The wear plate
35
is of conventional construction except for the fact that it has slots
36
extending between the bolt holes
37
therein (FIG.
5
). The slots
36
allow for fluid passage between and to the bolt holes
37
through the wear plate
35
(as later described). The webs
38
interrupting the slots
36
provide for structural integrity of the wear plate center area (and also allow for the convenient handling of the part). By overlaying the wear plate (
FIG. 5
) on the bearing/port section (
FIG. 6
) it can be seen that at the wear plate the fluid from the hole
25
is distributed for a significant distance about the circumference of the device (360° with the addition of a second groove
19
—dotted lines the bottom of FIG.
6
).
The particular wear plate is approximately 3.735″ in diameter and 0.22″ thick. A 1.2″ hole is located in its center. There are three 0.36″ width discontinuous grooves equally spaced on a 2.83″ circle around the outer circumference of the wear plate. At least one of the webs
38
between the slots
36
is preferably fluidically bypassed by the groove
19
in the housing
11
(and/or passages in manifold
40
). The two slots
36
shown extend between the bolt holes
37
approximately for 51.5° and a third 102.8° through the full depth of the wear plate. In the embodiment disclosed there is again inside contact between the bolt holes
37
and the bolts
90
to locate the wear plate
35
.
The main emphasis of the invention of the present application are the fluid passages which extend through the multi-plate manifold
40
between the port
28
and the valving area
71
outside of the orbiting valve
72
contained within the endplate
70
(the valve
72
itself is orbited by a extension
39
off of the wobblestick with the central opening
74
in such valve interconnected to the other port
27
via the central cavity
26
and the passageway
42
through the center of the rotor and manifold).
The manifold
40
is important in the preferred gerotor motor in that it serves three major purposes:
The first purpose is to transfer fluid continuously from the two ports
27
,
28
to the valving area
71
and central opening
74
of the valve
72
. This continual commutation demands an unimpeded fluid passage through the manifold via openings, preferably at least as large as the later described valving passages in order to not impede the volumetric efficiency of the gerotor motor. This dual fluid connection requires two separate sets of fluid passageways in the manifold
40
.
The second purpose of the manifold
40
is to interconnect the valving area
71
and central opening
74
of the valve
72
selectively to the expanding and contracting gerotor cells of the gerotor structure
30
as the device is operated. This valving operates through a single set of bi-directional passageways extending also in the manifold
40
.
The third purpose of the manifold is to provide physical room for the orbiting offset of the valve from the rotor
31
and the rotational axis of the driveshaft
21
.
In respect to the first purpose, the interconnection between the port
27
to the central opening
74
of the valve
72
in the embodiment disclosed is a simple hole
42
, which hole extends straight through the manifold
40
from one side to another. The size of this central hole is sufficient so as to not serve to impede fluid flow through the gerotor motor while at the same time being small enough so as to not interfere with either the other passages in the manifold or to interconnect the central opening
74
with the valving area
71
bi-passing the valve
72
. By having the hole in the manifold plate immediately laterally adjoining the wobblestick
34
larger than the next plate there is an increased clearance for the wobblestick (as well as an additional surface edge for the localization of the wobblestick).
The interconnection between the other port
28
and the valving area
71
through the manifold
40
is of a more unique configuration. A reason for this is that the passages
43
incorporate the areas
44
about the bolts
90
, intermediate areas
45
and internal areas
46
.
The utilization of the areas
44
surrounding the bolts
90
for the passage of fluid enables the manifold
40
to have a smaller diameter than if a separate passage(s) was incorporated outside of the diameter of the bolt circle while not compromising volumetric efficiency, physical strength and/or longevity (as separate radially offset passages might produce). In the particular embodiment disclosed, the areas are created mostly by extending the edges of the bolt holes radially of the diameter of the bolts (FIG.
13
). This is accomplished in the preferred embodiment by using radii different than that of the bolt spaced from the axis of such bolt to provide for areas adjacent to the outer diameter of such bolts. There is preferably always at least some contact between the bolts and the various plates that make up the manifold at the inner (and preferably also outer) sides of the bolts
90
so as to allow the bolts to physically retain the manifold
40
in place and intact against high pressure (because the manifold is typically brazed, this contact serves to strengthen the interconnections between the plates thus allowing the use of smaller surfaces for brazing between plates). In the embodiment disclosed, this contact arranges from less than 10° on a surface (as at
44
a
) to substantially 180° contact (as at
44
b
). It is preferred that each bolt include both an inside and outside contact so as to retain the associated parts in their designed position. In this respect, it is noted that while some contact is shown in all plates to all bolts, contact therebetween can be omitted to individual bolts and/or plates as long as there is sufficient contact between the totality of bolts and the entire manifold
40
so as to retain same in physical position in respect to the housing
11
and gerotor structure
30
at the desired pressure range. Again inner contact equally spaced 360° about the device is preferred so as to contain the otherwise outward forces existent in the device with a compression type load near to the generation of forces.
The intermediate areas
45
serve to pass the fluid through the manifold
40
in addition to aiding in equalizing the fluid flow and pressure circumferentially about the manifold by bridging the webs
38
in the wear plate
35
and other webs between passages in the manifold plates. These intermediate areas
45
preferably interconnect at the outside bolt radius in order to maximize the distance between these intermediate areas and the later described valving passages (and the pins
49
).
The internal areas
46
serve to pass the fluid from the bolt circle and intermediate areas
45
to an inside area including the valving area
71
immediately surrounding the valve
72
. This facilitates the passage of fluid from the holes
44
to this valving area
71
. Preferably, the internal extent of the internal areas
46
is defined by the outer diameter of the valve
72
as it contacts the manifold
40
—any further internal extension would be covered by the valve and be of no substantive effect.
In all instances, preferably there is a significant overlap between the passages to the various plates to allow for the relative free passage of fluid therebetween. This allows for pressure and fluid flow equalization about the device. It is not necessary that the intermediate areas
45
be all symmetrically interconnected as long as in total they cooperate to further extend the fluid 360° about the valve
72
from the initial single hole
25
(contrast
44
c
with passage
44
d
in FIG.
11
).
The manifold itself is some 3.7″ in diameter and 0.60″ thick. The manifold is made up of a stack of eight plates pinned together by four 0.125″ diameter pins
49
located on a 2.750″ bolt circle prior to brazing. These pins localize the plates in respect to each other during the brazing operation as well as serving to allow for the radial forces to be more efficiently passed therein. In addition the various openings and passages
43
-
45
in the manifold
40
cooperated in total with the bolts
90
to physically localize the manifold
40
in respect to the housing while simultaneously creating fluid openings for the distribution of fluid from the hole
25
to the area
71
surrounding the valve
72
. This occurs because of the unimpeded areas in the various plates
50
-
54
that make up the openings in the manifold. The bolts
90
again preferably contact the inside surfaces of the manifold
40
to locate same.
The cell opening plate
50
is some 3.7″ in diameter and 0.075″ thick (0.150″ for the pair shown). Each plate
50
includes seven equally spaced holes some 0.322″ in diameter located on a 2.80″ bolt circle. Five of the holes are interconnected by a 0.135″ wide web beginning at a 1.475″ inside diameter. The inside connections between the holes and webs and the outside outer ends of the holes are extended to 0.188″ (from 0.158″ with 0.125″ radiused ends) to provide for a set of interior inside passages
81
and exterior outside passages
80
about these holes. As can be seen from
FIG. 13
the extension and radiusing of the ends of the holes provides for an outer passage
47
and an inner passage
48
that would not exist had the web
45
directly interconnected with holes the diameter of the bolts
90
(the holes shown are 0.325″ diameter containing 0.315″ diameter bolts both on a 2.80″ bolt circle). Two other holes have a 0.75″ extension some 0.135″ wide on the same inner diameter with 0.068″ radius ends extending bi-directionally thereof. The center hole is 0.95″ in diameter in the outer plate and 0.80″ in the inner plate.
The internal shift plate
51
is some 3.7″ in diameter and 0.075″ thick (0.150″ for the pair shown). The holes in the internal shift plate
51
are some 0.380″ in diameter spaced on a 2.845″ bolt circle. The seven holes are again equally spaced, again with a 0.135″ interconnecting web on a 1.475″ inner diameter and two holes with a 0.75″ extension (again with radiused inside and outside ends). The center hole is 0.80″ in diameter.
The connection plate
52
is 3.7″ in diameter and 0.042″ thick. It has a series of 0.380″ diameter holes on a 2.845″ bolt circle again connected by a 0.135″ wide web on a 1.475″ inner diameter and with the 0.75″ extensions (with radiuses) and a 0.80″ diameter inner hole.
The external shift plate
53
is 3.7″ in diameter and 0.075″ thick (0.150″ total). The plate
53
has a series of 0.380″ diameter holes spaced on a 2.845″ bolt circle. Five of the bolt holes are interconnected by a 0.172″ wide web on a 1.435″ inner diameter with radiused ends. There is an inner extension extending off of six of the bolt holes some 0.43″ wide extending inward to a 1.04″ inner radius. Two of these inward extensions are connected by a 0.19″ wide web extending outward from a 1.04″ inner diameter while a separate extension extends in respect to an additional bolt hole some 0.75″ long. All edge radii are 0.125″.
The valving plate
54
is 3.7″ in diameter and 0.075″ thick. It has a series of 0.380″ diameter holes located on a 2.845″ bolt circle. These holes are interconnected by a 0.175″ wide web with a 1.435″ inner diameter for the outward passages and a 0.19″ web and 1.040″ diameter for the inner passages. Again, the inward extensions are 0.43″ wide extending inward to a 1.04″ inner diameter and all edges are radiused to 0.125″.
The valving passages
60
are designed to minimize the restrictiveness of their opening to a single set of crossover openings
67
in the center of the manifold
40
.
The valve openings
61
are designed for a smooth transition between fluid connections in an orbiting valve type design. Towards this end the inner edge of a chosen valving opening blends in with the outer edge of an adjacent opening, thus to provide for a smooth transition in the valving process.
The external shift passages
63
and the external shift plate
53
begin with an outer section
64
which substantially matches that of the valving passages
61
. The internal section
65
of these same passages extend inwards toward the central opening
42
without a reduction in cross-sectional area while at the same time providing sufficient distance between adjacent passages that there is a proper sealing therebetween.
The crossover openings
67
in the connection plate
52
include the entire area which is common to both the external shift passages
63
and the later described internal shift passages
68
. These crossover openings
67
are thus the maximum cross-sectional size they can be effectively while still efficiently transferring fluid between the external shift passages
63
and the internal shift passages
68
.
The internal shift passages
68
in the internal shift plate
51
extend for the greatest distance they are thus the largest passages within the manifold
40
. The inner end
69
of the internal shift passages
68
match that of the crossover openings
67
while the outer ends
70
substantially replicate the expanding/contracting gerotor cells of the gerotor device. Again, these internal shift passages
68
are designed with a minimum clearance therebetween so as to maximize the size of such passages.
The cell openings
171
in the cell opening plate
50
include a main section
172
which is substantially centered on the expanding/contracting gerotor cells. A small additional extension
73
provides for auxiliary lubrication of the cylinders
33
in the gerotor motor by extending substantially to the center of the area off of axial ends of such cylinders
33
. Again, the size of these cell openings
171
substantially overlap the internal shift passages
68
so as to provide for the efficient fluid passage therebetween.
In order to further increase the amount of fluid passing through the manifold, the cell opening plate
50
, the internal shift plate
51
and the external shift plate
53
are used in multiples, thereby to increase the cross-sectional area of the valving passages
60
extending therein, thus to further increase the volumetric efficiency of the gerotor motor.
The end plate
70
completes the housing
11
by aiding to seal the area
71
surrounding the valve
72
against the manifold
40
. The end plate is substantially 3.6″ in diameter and 1.17″ long with a series of 0.315″ diameter holes on a 2.8″ bolt circle for the bolts
90
.
Although this invention has been described win its preferred form with a certain degree of particularity, numerous changes can be made without deviating from the following claimed invention. For example an inside contact between the bolts
50
and the various openings
43
-
45
in the manifold
40
are utilized to retain the manifold in position in respect to the remainder of the housing
11
. If desired outside contact, a combined inside/outside contact, a limited number of dedicated through bolts or other contacts could be utilized without deviating from this invention. Additional example the passages within the manifold can be modified to provide for a 360° transfer of fluid entirely within the manifold. This could be accomplished by modifying the two plates
50
,
51
(
FIGS. 8 and 9
) as plates
150
,
151
(
FIGS. 14 and 15
) and/or the plates
53
,
54
(
FIGS. 11 and 12
) as plates
153
,
154
(FIGS.
16
and
17
). It is not preferred to modify the cross-over plate
52
due to the single thickness limited available area in this plate. Other changes are also possible.
Claims
- 1. A fluid passage for a manifold having bolts extending through holes therein, the fluid passage comprising a radially extended area, said radially extended area extending off of a first portion of at least one hole surrounding a bolt, said at least one hole having a second portion surrounding said bolt, said second portion of said hole having an inner surface and said inner surface of the second portion of said hole being in contact with the bolt.
- 2. A fluid passage for a manifold having bolts extending through holes therein, the fluid passage comprising a radially extended area, said radially extended area extending off of at least one hole surrounding a bolt, there being two adjoining holes with radially extended areas and two radially extended areas of said two adjoining holes forming an interconnection passage connecting same,said at least one hole surrounding a bolt having an inner surface and said inner surface being in contact with the bolt.
- 3. The fluid passage of claim 2 characterized in that said interconnection passage connects the outer extent of said two adjoining holes.
- 4. A fluid passage for a manifold having bolts extending through holes therein, the fluid passage comprising a radially extended area, said radially extended area extending off of at least one hole surrounding a bolt, said at least one hole having two radially extended areas, said two radially extended areas extending symmetrically in opposing radial directions,said at least one hole surrounding a bolt having an inner surface and said inner surface being in contact with the bolt.
- 5. The fluid passage of claim 4 characterized in that said two radially extended areas extend off of the outer extent of said at least one hole.
- 6. A fluid passage for a manifold having bolts extending through holes therein, the fluid passage comprising the holes surrounding the bolts,an interconnection passage, said interconnection passage connecting two of the holes, and the fluid passage including said interconnection passage.
- 7. The fluid passage of claim 6 wherein the bolts have an inside surface and characterized in that the holes contact the bolts at the inside surface thereof.
- 8. The fluid passage of claim 6 characterized in that said interconnection passage connects to the outer extent of two of the holes.
- 9. The fluid passage of claim 6 characterized by the addition of an internal area, said internal area extending off of at least one of the holes towards the axial center of the manifold.
- 10. The fluid passage of claim 6 characterized in that the manifold is of multi-plate construction with said interconnection passage in at least two plates.
- 11. The fluid passage of claim 10 characterized in that said interconnection passages overlap between plates.
- 12. The fluid passage of claim 11 characterized in that said interconnection passages include some overlapping through all plates of the manifold.
- 13. The fluid passage of claim 6 wherein the device has a passage in the housing to a port and characterized by the passage to the port being located between two of the bolt holes,a groove, said groove being in the housing and said groove connecting the passage to said two bolt holes.
- 14. The fluid passage of claim 13 wherein the housing includes a wear plate and characterized in that said groove is in the wear plate.
- 15. A fluid passage of claim 6 characterized in that said interconnection passage connects two holes, and said two holes being adjacent.
- 16. A fluid passage for a manifold having bolts extending through holes therein, the fluid passage comprising the holes surrounding the bolts, the holes having an outer edge respectively, said outer edge being extended radially of the bolts,an interconnection passage, said interconnection passage connecting at least two of the holes, and the fluid passage including said interconnection passage.
- 17. The fluid passage of claim 16 wherein the bolts and holes have diameters and characterized in that the diameter of the holes is greater than the diameter of the bolts.
- 18. The fluid passage of claim 16 characterized in that said interconnection passage connects the outer extent of said at least two of the holes.
- 19. The fluid passage of claim 16 characterized in that the outer edge of a given hole is extended in both radial directions in respect to such given hole.
- 20. The fluid passage of claim 16 wherein the manifold has a surface confronting a valve and characterized by the addition of an internal area, said internal area extending in the surface of the manifold off of at least one of said holes towards the axial center of the manifold.
- 21. The fluid passage of claim 20 characterized in that said internal areas exist between two of the holes.
- 22. The fluid passage of claim 20 characterized in that said internal area extends between two of the holes.
- 23. The fluid passage of claim 16 characterized by the addition of a radially extended area, and said radially extended area extending off of one of said holes in the opposite direction as said interconnection passage.
- 24. A fluid passage of claim 16 characterized in that said interconnection passage connects two holes, and said two holes being adjacent.
- 25. In a hydraulic device having a valving opening to a gerotor cell in a surface adjacent to a stator roll with an end,the improvement of an extension, said extension being in the surface, said extension extending laterally off of the valving opening, next to the end of the stator roll connecting same to the valving opening.
- 26. In a hydraulic device having bolts and passages, the passages comprising an inner unidirectional passage, an out unidirectional passage, and a system of bi-directional channels, the improvement of the passages being located next to the bolts, said inner unidirectional passage being the central cavity, said outer unidirectional passage including the holes surrounding the bolts, and said system of bi-directional channels being located between said inner and outer unidirectional passages.
- 27. The improvement of the system of fluid passages of claim 26 characterized in that said outer unidirectional passage includes radially extended areas, said radially extended areas extending off of at least one hole surrounding a bolt.
- 28. The improvement of the system of fluid passages of claim 27 characterized in that there are two adjoining holes with radially extended areas and two radially extended areas of said two adjoining holes forming an interconnection passage connecting same.
- 29. The improvement of the system of fluid passages of claim 28 characterized in that said at least one hole has two radially extended areas and said two radially extended areas extending symmetrically in opposing radial directions.
- 30. The improvement of the system of claim 26 characterized in that said outer unidirectional passage including an internal area, said internal area extending off of at least one hole towards the axial center of the manifold.
- 31. The improvement of the system of claim 26 wherein the device includes a stator roll having an end and characterized in that said bi-directional channels have a valving opening, an extension, said extension being in the surface, said extension extending laterally off of the bi-directional channels respectively next to the end of the stator roll at the valving opening.
US Referenced Citations (6)