CA1231585A - Rotary gerotor hydraulic device with fluid control passageways through the rotor - Google Patents

Abstract

Abstract of the Disclosure A rotary fluid pressure device is disclosed compris-ing a housing having fluid inlet and outlet means and enclosing a gerotor having an internally toothed member and a coacting externally toothed member having a less number of teeth than the internally toothed member and having its axis positioned eccentrically relative to the axis of the internally toothed member. A wobble stick in the housing has a first end con-nected to the axial drive shaft and a second end connected to the gerotor member having the orbital movement. The housing has one set of passageways communicating at all times with the ex-panding and contracting gerotor cells. The gerotor member having orbital movement is, in addition to its usual function, a valve with two travel passageways, one travel passageway coaxially surrounding the other passageway. These two travel passageways communicate at all times part of the set of passage-ways in the housing with only one fluid inlet or outlet while communicating other of this same set of passageways with the other fluid inlet and outlet.
A star-pointed annulus increases commutation fluid flow.
A laminated plate design facilitates the construction of the porting passages.

Description

3~L5~rj This application is a division of Canadian 1 Application No. 422,267 filed February 23, 1983 for ROTARY GYRATOR HYDRAULIC DEVICE WITH FLUID CONTROL
PASSAGEWAYS THROUGH THE ROTOR.
An object of this invention is to provide a rotary fluid pressure device including a gyrator having a fixed stators inside of which is an orbiting and rotating rotor.
The rotation of the orbiting rotor member provides the output or input at the shaft member. This rotor has a continuous ring valve on one side and both of the supplies of intake and lo exhaust pressure fluid are on the opposite side. A star-pointed annuls increases commutation fluid flow. The second embodiment shows again a fixed stators with an orbiting rotor with the rotating component of the rotor used at the output shaft; but in this embodiment the intake is on the internal diameter of one side of the rotor member with balanced area grooves in communication with the first named intake and ox-Hess grooves on the opposite side of the rotor so as to provide a hydraulically balanced rotor.
An added object of this invention is to provide a pros-sure loaded commutator ring urged with a wave spring for initial contact, together with a drive pin connected between the rotor and the commutator ring.
Another object of the invention is to provide a pros-sure loading plats in the end cover of the housing so as to cause a pressure balance providing a head force towards the manifold and gyrator set.
The present invention reduces the number of manufac-luring operations necessary to make hydraulic pressure devices.
The devices made in accord with this invention are simple, felt-able and efficient.

1 Another object of this invention is to provide a ho-draulically balanced rotor.
Still another object is to reduce the wear of and cool the wobble stick drive connections.
Another object of the invention is to increase the commutation fluid flow.
Other objects and advantages of the present invention will be apparent from the accompanying drawings and the de-ascription. The essential features will be set forth in the appended claims.
Brief Description of the Drawings FIGURE 1 is a central sectional view through a first embodiment of this invention;
FIGURE 2 is a sectional view taken along the line 2-2 of FIGURE l;
FIGURE 3 is a sectional view taxes along the line 3-3 of FIGURE l;
FIGURE 4 is a sectional view taxes along the line 4-4 of FIGURE l;
FIGURE 5 is a sectional view taken along the lint 5-5 of FIGURE l;
FIGURE PA is a fragmental sectional view taken along the line AYE of FIGURE 5;
FIGURE 6 is a sectional view taken along the line 6-6 of FIGURE l;
FIGURE 7 is a sectional view taken along the line 7-7 of FIGURE l;
FIGURE 8 is a central sectional view through thy second embodiment of this invention;
FIGURE 9, 10 and 11 are respectively sectional views taken along the lines 9-9, 10-10 and 11-11 of FIGURE 8, I

1 FIGURE 12 is a fragmental sectional view taken at the right hand end of FIGURE 1 and showing a pressure loaded commute-ion ring; while FIGURE 13 is a fragmental sectional view taken at the right hand end of FIGURE 1 and showing a pressure loading plats in the end cover;
FIGURE 14 is a central sectional view like FIGURE 1 but including a star pointed annuls;

FIGURE 15 is a sectional view taken along line 15-lS in FIGURE 14i FIGURE 16 is a sectional view taken along line 16-16 in FIGURE 14;
FIGURE 17 is a central sectional view of a hydraulic device like FIGURE 8 having shortened through passage and dip-firing manifold passages;
FIGURE 18 is a sectional view of the hydraulic device of FIGURE 17 taken along lines 18-18 of that FIGURE;
FIGURE 19 is a sectional view of the manifold plate of FIGURE 17 taken generally along lines 19-19 of that FIGURE;
FIGURE 20 is a central sectional view like FIGURE 14 of a bilateral ported hydraulic device;
FIGURE 21 is a sectional view of the manifold plate of the bilateral ported hydraulic device of FIGURE 20 taken goner-ally along lines 21-21 of that FIGURE;
FIGURE 22 is a central sectional view like FIGURE 8 of an inverse valved hydraulic device;
FIGURE 23 is a sectional view of the manifold plate of the inverse valved hydraulic device of FIGURE 22 taken generally along lines 23-23 of that FIGURE;
FIGURE 24 is a central sectional view like FIGURE 14 of a manifold plate ported hydraulic device;

assay 1 FIGURE 25 is a sectional view of the manifold plate of FIGURE 24 taken generally along lines 25-25 of that FIGURE;
FIGURE 26 is a sectional view of the manifold plate of FIGURE 24 taken generally along lines 26-26 of that FIGURE;
FIGURE 27 is a sectional view of the channel closure plate of FIGURE 24 taken generally along lines 27-27 of that FIGURE;
FIGURE 28 is a sectional view of the end plate of FIGURE

24 taken generally along lines 28-28 of that FIGURE;

FIGURE 29 is a central sectional view similar to FIGURE

14 of an intermediate plate gyrator porting. The gyrator is contained in a power steering unit. The unit is of multi-plate construction;
FIGURE 30 is a view of the porting passages of FIGURE 29 taken generally along lines 30-30 of that FIGURE;
FIGURE 31 is a view of the porting passages of FIGURE
29 taken along lines 31-31 of that FIGURE;
FIGURE 32 is a view of the porting passages of FIGURE
29 taken generally along lines 32-32 of that FIGURE;
I FIGURE 33 is a view of the porting passages of FIGURE
29 taken generally along lines 33-33 of that FIGURE;
FIGURE 34 is a view of the porting passages of FIGURE
29 taken generally along lines 34-3~ of that FIGURE;
FIGURE 35 is a central sectional view of a power steer-in unit similar to that of FIGURE 29. This FIGURE 35 unit fur-then utilizing multi-plates to simplify the construction of the body of the unit;
FIGURE 36 is a view of the plates of FIGURE 35 taken generally along lines 36-36 of that FIGURE;

FIGURE 37 is a view of the plates of FIGURE 35 taken 11.~3.1L':~5 1 generally along lines 37-37 of that Figure';
FIGURE 38 is a view of the plates of FIGURE 35 taken generally along lines 38-38 of that FIGURE; and FIGURE 39 is a view of the plates of FIGURE 35 taken generally along lines 39-39 of that FIGURE.
Those familiar with this type of apparatus will under-stand that while the present invention is being described as a pump using a fluid inlet and a fluid outlet, nevertheless, the same structure may be used as a motor by merely reversing the fluid inlet and outlet so that the high pressure fluid now en-lens at what was previously the inlet and the device operates as a motor.
In the description and claims occurring hereinafter, the term "housing" is used to include not only the main housing mom-berm but also the pressure plate, gyrator set, manifold and end cap, all of these latter parts being connected to the main housing portion by bolts.
Referring now to FIGURE 1, the first embodiment of this invention comprises a main housing unit 20 having a radially flat inner end to which is respectively attached a wear plate 21, a gyrator set 22, a manifold 23 and an end cap 24, all of these being secured together by bolts 25, which are shown in the van-ions sectional views but omitted from FIGURE 1, but those skilled in this art will recognize that the bolts have heads pressing against the outer right hand end of the end cap 24 and extending through the members 21, 22 and 23 and threaded tightly into the main housing portion 20. Sealing rings 26 seal all of the members against leakage between them.

The gyrator set 22, best seen in FIGURES 1 and 4, come proses an internal toothed member 27 which is a stators inside 3 to 1 of which a coating externally toothed member 28, a rotor, which rotates about its own axis A as seen in FIGURE 4, but which is eccentric relative to the center of the stators 27 by the distance shown between A and B, on the line of eccentricity C, and the rotor orbits about the center B. During this move-mint of the rotor and stators a series of cells 29 and aye form a series of cells of constantly changing size between the rotor and stators the size of the cells becoming greater on one side of the line of eccentricity, and the cell size becoming smaller on the opposite side In FIGURE 4 the minimum size cell at aye approaches zero. The rotor rotates in the direction of the arrow shown in FIGURE 4. The rotor has two flat axial end surfaces.
The inlet means to the housing is indicated at 30. The fluid outlet means is shown at 31. The inlet means is connected by means indicated only in dot dash lines through a continuous annuls or distribution channel 32 in the main housing portion 20. This annuls opens through the wear plate 21 which has a number of through openings or fluid trivialize 33, the number of which is not important, but sufficient to take care of the flow of fluid necessary. These openings 33 are connected ho connecting passages aye to the annuls or annular ring transfer channel 34 of smaller diameter on the opposite face of the wear plate and opening into the rotor cavity toward the gyrator 22.
The annuls 34 may be ring-shaped (FIGURES 1 and 3) or star-pointed (FIGURES 14 and 16). The ring-shaped annuls 34 is symmetrical - a channel of uniform diameter and depth The star-pointed annuls 34b, in contrast, has a shape dictated by the area swept by the passageways 37 through the rotor 2B during the rotation of the rotor pa. The star-pointed annuls 34b is of varying diameter and depth - widest and deepest at the points I

1 of the annuls 34b. The connecting passages aye intersect with the star-pointed annuls 34b at the points of the annuls 34b.
The internal teeth aye on the stators 27 are provided by cylinders aye inserted in recesses 27b over 1$0 in circumfer-once so as to maintain the cylinders aye in the positions shown in FIGURE 4. It will be understood that the cylinders aye ton-minute at the level of the opposite faces of the stators 27. The rotor 28 has external teeth which are formed to fit almost ox-aptly between the internal teeth of the stators as shown in FIG

USE 4. The rotor 28 has an open center 35 surrounded by a seal-in strip 36 which is uninterrupted circumferential and fat-orally outside of which is an annular liquid intake passageway 37. The axis of rotation for the wobble stick 38 is marked A in FIGURE 4. The axis of rotation for the orbiting movement of the wobble stick 38 relative to the stators is indicated at B
in FIGURE 4. The line C passing through A and B is herein India acted as the line of eccentricity. The movement of the rotor herein described is as indicated by the arrow D in FIGURE 4.
During this rotation the cells 29 on the left hand side of the line of eccentricity increase in size gradually while the cells 29 on the right hand side of the line of eccentricity gradually decrease in size as indicated in FIGURE 4. The rotor functions as the main valve for the device. Six travel passageways or holes aye are evenly spaced around the annuls 37 extending linearly through the rotor parallel to the axis of the rotor. These project radially inwardly from the annuls or annular channels 37 as seen at 37b, in one endowment this being about 1/8 of an inch projection. The other travel passageway is generally on the central axis of the rotor, in the structure disclosed around the wobble stick-rotor device connection. There are sufficient z 3 to 1 openings in this type of drive connection that fluid flow is relatively unimpeded by the spline-gear interfaces. The trays-for channel 34 communicates with the annular channel as the de-vice is operated.
A manifold 23 connects the rotor valve with the gyrator cells. The manifold 23 will be best shown in FIGURES 5, PA, an 6. Seven parallel through openings to extend through the rotor facing surfaces of the manifold I parallel to its axis. This set of openings, as best seen in FIGURES 5 and 6, have a peculiar cross section. These openings 40 will be herein described as "double-trapezoidal". Referring to FIGURE 5, it will be seen that one of these openings appears substantially like two tripe-voids facing each other with no middle partition and having opt posit ends which are not quite parallel but instead are radial.
The radially inner side of each opening is composed, not ox straight lines, but of lines slightly concave inwardly meeting in a slight peak at the center aye. The outer wall of this opening radially, as seen in FIGURE 5, may be composed of two straight lines meeting in the center or preferably a single line slightly convex radially outwardly. The size of each of these openings is such as to fit in the opening, seen in FIGURE 4, between two of the cylindrical openings aye in a circumferential direction and between the central opening and the annuls 37 in a radial direction. These openings 40 are swept by the travel passageways in the rotor as the device is operated. This performs the primary valving function of the device. Each of the openings 41, as seen in FIGURES 5 and 6, of which there are seven evenly spaced, on the side of the manifold toward the gyrator are connected by fluid passageways aye and 42 sloping inwardly and downwardly to one of the openings 40 just described.

I

1 The manifold 23, as seen in FIGURE 6, shows seven in-dined passageways 42 in solid lines which cocci with the struck lure described in connection with the openings 41, passageways aye and openings 40 as previously described. These coating passageways are shown in broken lines in FIGURE 6 to show the cooperation. Seven of such passages 42 are provided extending part way through the manifold from side to side. These are at a slight angle to the axis of the gyrator and are spaced at a diameter to register, as shown in FIGURES 5 and 6. It will thus ye seen that each passageway 42 in the manifold mates with one of the passages aye half-way through the manifold so that each of the seven passages 40 combines with one of the passages aye, 42~
The elongated rigid wobble stick 38 is clearly seen in FIGURE 1 and shown in section in FIGURES 2 and 3. One end of the wobble stick has a splint connection 44b with the drive shaft 44. It will be noted that this shaft has a solid outer end and a hollow inner end as indicated at aye. The opposite end of the wobble stick has a splint connection 44c in a eon-trial bore in the rotor 28. These splint connections are pro-voided in such a manner that the wobble stink may rotate and orbit around the center axes A, B and that fluid can continuously flow over and around them. The exhaust passageway includes the open center 35 of the rotor over and around the wobble stick-rotor drive connection and the open center aye of the wear plate and the hollow aye, and is completed by four radial past sieges 45 and 46 which are connected as shown in dot-dash lines, with the outlet 31.
Suitable needle bearings are shown at 47 and 48 support-in the drive shaft 44 in the main housing portion 20. Also go _ 3 to 1 suitable sealing means as shown at 49 and 50 are. provided where the drive shaft passes out of the main housing portion 20.
This embodiment has been described as a pump utilizing the drive shaft 44 for the attachment of power which would cause intake of lower pressure fluid at 30 and exhaust of higher pros-sure fluid at 31. As previously explained, reversing the con-sections 30 and 31 will cause the device to operate as a motor producing power on the drive shaft 44.
The operation of the first embodiment as a pump Jill now be described. Power is supplied to the protruding left end of the drive shaft 44 as seen in FIGURE 1. This rotates the shaft, the wobble stick 38, the rotor 28, and also causes the rotor to orbit about the stators 27. This causes the cells 29 to the left of the line of eccentricity C to gradually increase in size causing a suction at the intake 30. The cells 29 on the right hand side of the line of eccentricity C in FIGURE 3 are also caused to progressively decrease in size thus causing the fluid under increased pressure to exhaust at the outlet 31.
The incoming fluid from intake 30 passes through the annular channel 32, the passageways aye to the annular channel 34, then through the rotor 28 through the annular channels 37 and the cry-lindrical holes aye, then through the double trapezoidal open-ins 40 in the manifold 23, then through the passageways aye and 42 in the manifold and through the openings 41 in the manifold and rotor and thus into the expanding cells 29. Other cells 29 are exhausted back through other openings 41 and other passage-ways 42 and aye and other double trapezoidal openings 40 in the manifold into the open center 35 of the rotor. The fluid then flows over and around clearances in the wobble sti~k-rotor drive connection, cooling and lubricating it, through the l opening aye, through the hollow portion aye of the shaft and through openings 45 and 46 and thus out through the outlet 31.
If the rotary fluid pressure gyrator device incorporates the star-pointed annuls 34b the commutation fluid passage is more direct and less constrained than with a ring-shaped annuls 34. Please note that other commutation channels in the gyrator device can also benefit from being star-pointed -- for example annular channel 37.
The second embodiment of this invention is shown in lo FIGURES 8, 9, lo and 11. FIGURE 8 is a central sectional view through the second embodiment with the bearings and seals resew-sling those seen in FIGURE 1 omitted for simplification of the drawings.
The main housing portion 60 has secured to it a wear plate 61, a gyrator set 62, a manifold 63 and an end cap 64, all secured rigidly together by a plurality of bolts 65 ox-tending from the right hand end of the device as seen in FIGURE
8 into threads in the main housing portion 60. The main housing portion has an intake 66 connected by a passage 67 through I the housing portion 60 with a continuous annuls chamber 68, which communicates with a plurality of radial openings 69 which lead inwardly to a hollow portion aye of a drive shaft 70 which is rotatable mounted in the housing portion 60. An eon-grated rigid wobble stick 71 has a splint connection aye at one end with the drive shaft 70 and another splint connection 71b at the opposite end with the rotor member of the gyrator set 62. The splint connections aye and 71b are so shaped as to permit the rotation of the wobble stick while at the same time permitting it to follow the orbiting movement of the rotor in the stators as will presently appear.

~3~5~Cj 1 The wear plate 61 has a circular opening aye which permits the necessary movement of the wobble stick 71 and at the same time forms part of the intake passageway for fluid.
Six pairs of intake passageways 82 and 83 extending through the rotor 72 connecting the circular opening aye in the wear plate 61 with the annular passageway 84. The annular passageway 84 opens towards the manifold 63.
FIGURE 17 is of a device like that shown in FIGURE 8.
In the device of FIGURE 17 the intake passageway 83 terminates in the area of the splint drive connection 71. This cools and lubricates this connection. In addition the manifold plate AYE
uses surface channels AYE to connect the openings 40 and 41, respectively.
The intake AYE and passage AYE are of a greater diameter than in FIGURE 8. There are two staggered rows of radial openings AYE, 69B, in the drive shaft 70. See FIGURE 18.
These in combination allow for the unimpeded fluid input into the area about the wobble stick without the need of a continuous annuls chamber 68 as in FIGURE 8.
The manifold plate AYE, instead of using angled holes 78 to connect the pairs of openings 40-41 respectively, uses channels AYE let into the surface of the manifold plate AYE
away from the rotor. See FIGURE 19. The end plate covers the open side of the channels AYE. See FIGURE 17.
The gyrator 62 is best seen in FIGURE 9. It comprises a stators aye which has a plurality of internally extending teeth formed partly by direct formation in the stators but also in part by six cylindrical members 62b which are firmly held in recesses 62c which extend for a distance greater than the ray dips of each of the cylinders 62b so that they are held firmly il.Z3~1l5~S

1 in the position shown in FIGURE 9. A rotor 72 is shown having a plurality of externally extending teeth aye which are shaped to fittingly cocci with the internally extending teeth 62, aye and 62b, these external teeth being one less in number than the internal teeth previously described. The rotor has an axis E
which is eccentric relative to the axis F of the stators and the line G passing through points E and F is herein designated as the line of eccentricity. The rotor is provided with a generally annular ring 84 forming part of the intake passageway for fluid. This passageway is concentric around the axis E.
Inside the annular ring 84 is a circular opening 74, also concern-Eric, for the exhaust of fluid from the rotary fluid pressure device.
Referring now to FIGS. 9, 10 and 11, FIG. 11 shows the face of the manifold toward the gyrator structure 62. Centrally there is the exhaust opening 75 which communicates with the ox-haunt opening 74. m the next circle, and concentric, are seven rotor communicating openings 76, and in an outer concentric air-ale are seven passageway openings 77 so positioned that they co-operate circumferential with the cells 80 which are formed unchanging fashion battalion the rotor and the stators as seen in FIG. 9.
FIG. 10 shows the face of the manifold 63 toward the end cap 64. This shows the through passageways 76 each connected to one of the openings 77 by means of angular passageways 7 and 79, each pair of which joins at an opening aye.
The cooperation of these parts is shown in dot-dash lines in FIG. 9 at 81. This shows one of the openings 77 in position to cooperate with a cell aye at the top of FIG. 9 and it is in cooperation through passageways 78 and 79, here shown I S

1 diagrammatically, with one of the openings 76, which you might say is about two and one-half positions away going around the circle. It will now be seen how the radially outward openings aye in the annular ring 84 cooperate with the communicating passageways 76. There are six of the formations aye and each comprises a central, radially outermost portion 84b which ox-tends substantially circumferential and at each end of this outermost portion is a radially and circumferential inwardly sloping portion 84c which extends to a radially innermost sepal rating portion 84d. Each of the passageways 76 is herein de-scribed as double trapezoidal in section inasmuch as the opposite halves of the section are approximately trapezoid with their wider edges opening toward each other in the center. It will now be seen in FIG. 9 that when the dead pocket aye at the top of FIG. 9 is in communication with its associated opening 77, then the other end of the connection through the 78,79 connection and shown at 76 in dot-dash lines, will illustrate how the exhaust pocket related to cell aye is shut off before the fluid is trays-furred from the associated intake pocket 76. This gives the dead center pocket a higher pressure than the supply at 66 because the fluid is trapped at that particular moment This higher pros-sure causes the rotor 72 to seal better against the cylindrical members 62b on the opposite side of the axis. This higher pros-sure in cell aye also provides oil to the pivot roll near the upper dead center in FIG. 9 whereby the rotor floats on a hydra-dynamic oil film thus giving a hither mechanical efficiency out-put. It will now be seen that the shape of each of the portions aye of the annular ring 84 match fairly well with the radially outer edges of the double trapezoidal passageways 76.
A balancing ring 86 is on the opposite side of the rotor l from the annular ring 84. Small passages 87 through the rotor connect the balancing ring 86 to the opening 74. The balancing ring 86 equalizes the hydraulic pressure on the rotor 72.
` It should now be apparent how the operation of this device as shown in FIGS. ill operates. Power is applied to the shaft 70 causing the rotor 72 to rotate in the stators aye in the direction of the arrow shown in FIG. 9. The intake flow is from the inlet 66 through passageways 67 Ed 68, then through the hollow shaft portion aye and through the central opening aye in the wear plate. Then the flow is through passageways 82 and 83 to toe annular passageway 84 which opens toward the manifold 63. Then the flow passes through an opening to past siege 76 on one side of the eccentricity line G through the manifold passages 78, 79 to one of the openings 77 which is in communication with one of the cells 80 between the rotor and stators Meanwhile, one of the cells 80 on the other side of the eccentricity line G communicates back to the appropriate passageway 76 and back through the manifold 63 to the exhaust passageways 74, 75 and 85 to exhaust.
FIGURE 12 shows a portion of the right hand end of Fig 1 where the same parts are given the same reference numbers.
Otherwise, the device operates as descried in connection with FIG; 1. However, in FIG. 12 there has been added a pressure plate 90 inserted in a suitable recess in the end cap 240, and the end cap is pushed toward the left as viewed in FIG. 12 by means of pressure admitted through lines 91, connected with the exhaust 45, and line 92 connected with the intake 30. Each of the lines 91 and 92 has adjacent the pressure loading plate 90 a ball check valve 93 so that the loading plate 90 is always pressed inwardly toward the manifold 23 and the gyrator set 22 ~.23.~

1 beyond it. This provides for a head force towards the manic fold and rotor set. This will take care of any wear between the engaging rubbing portions 22 and 23.
FIG. 13 also shows a portion of the right hand end of FIG. 1 and all of the same parts are given the same reference characters. The added feature here is a pressure loaded come mutator ring 95 which extends inwardly, toward the left in FIG.
13, against a shoulder 96 with a wave spring 97 circular in shape and pressed between the commutator ring and the shoulder 96 to give an initial pressure. The wave spring is made of spring metal which weaves back and forth from a generally common plane as one goes around the circle. A seal 98 prevents leakage be-tweet the parts. There is provided a pin connection 99 which as seen in FIG. 13 is in general an axial extension of the splints 440b connecting the wobble stick 380 and the rotor of the gyrator set 22. This pin fits between the splints 440b and extends into a suitable opening aye in a portion of the commute-ion ring. This pin connection is somewhat loose so as to use the rotational component of the rotor as a means of timing the opening and closing of the connection indicated in dot-dash lines in FIG. 9. s FIG. 20 is of a bilateral ported hydraulic device.
In this device the inner travel passageway instead of running through the open center 35 of the rotor doubles back through a series of holes 100 in the manifold plate 23B to exit the gyrator device through port 101.
The holes 100 extend through the manifold plate 23B
about the central axis A' of the gyrator device. The wobble stick 38 makes any physical contact that it does with the manic fold plate 23B in the center of the circle defined by Halsey. See FIGURE 21.

1 Due to the pressures and volumes of fluid in motion in the gyrator device, there is a constant back water type fluid flow at all times over the wobble stick 38 - rotor drive connect lion 44c and throughout the central cavity 102 of the gyrator device. This fluid lubricates and removes contaminants from the gyrator device.
FIGURE 22 is of an inverse valved hydraulic device.
In this inverse valved device an outer ring channel 103 on one side of the rotor AYE is connected through a diagonal passageway 104 to the open center 35 of the rotor. A star shaped annuls 34 communicating with the outer ring channel 103 connects the fluid passageway to one of the fluid ports 30. The other fluid passage is a second ring channel 105. Another star-shaped an-nulls 106 communicating with the second ring channel 105 connects this fluid passage to the other of the fluid ports 107. This annuls 106 is on the manifold plate 23C between openings 40 and 41. See FIG. 23. These openings 40 and 41 are connected together respectively by a series of channels 108 on the oppo-site side of the manifold plate 23C). A series of holes lQ9, the location of which is not critical, extend from the annuls 106 through the manifold plate 23C and through the channel do-sure plate 110 to connect with cavity 111. The port 107 is con-netted to the cavity 111.
In operation the open center 35 of the rotor and the second ring channel 105 selectively communicate with the manic fold openings 40 to valve the gyrator device.
FIGURE 24 is of a manifold plate ported hydraulic de-vice. In this device both the porting commutation and the valving occur between a single surface of the rotor and the manifold plate 23D.

1 In this device port 112 connects through ring channel 113 in the end plate 115, and holes 114 through the closure plate 116, median plates 117, 118 and manifold plate 23D to star-shaped commutation annuls 119. The annuls 119 communicates with ring channel 37B on the rotor. Port 120 connects through hole 121 in the closure plate 116 to the series of holes 122 in the median plates 117, 118 and the manifold plate 23n. The series of holes 122 communicate with the open center 35 of the rotor.
Passages AYE and the other ring channel 37 hydraulically balance the rotor for fluid pressure in the ring channel I
The opposite end of the open center of the rotor hydraulically balances the open center fluid passage.
The manifold plate has openings 41 and 41. openings 40 extend through the manifold plate. Holes 127 extend off of openings 41 through the manifold plate. Respective pairs of openings 40 and holes 127 are connected together by a series of channels 108 on the median plate 117~
In operation the ring channel 37 and the open center 35 of thy rotor selectively communicate with openings 40 to valve the device.
The actual porting in the manifold ported hydraulic device of FIGURE 24 is accomplished through the use of a series of successive plates 115-118 and 23D. Each ofthe~plates is de-signed for ease of individual manufacture. See FIGURES 25-28.
During assembly each plate is located in proper sequence in no-spent to the other plates to together form the porting passages of the device.
If necessary to insure an acceptable quantity of leakage between neighboring passageways sealing compound can be inserted -lo-~.~23~1 3 1 between the plates, the plates after assembly may be brazed together -to form a single unit or other appropriate steps taken.
FIGURE 29 is of a m~lti-plate intermediate plate ported hydraulic device. The device is disclosed in a power steering unit 127. FIGURE 35 is of a similar unit aye having multi-plate body construction. The fluid passages within these multi plate construction devices are identical in function. The de-vices will be described together.
The fluid recesses 128, aye are arranged about the slide member 129, aye in a cylinder 2(C2), return 2~R2), Cal inter l~Cl), media l(Ml), pressure 2(P23, return l(Rl~ and pressure l(Pl) layout.
The cylinder l(Cl) and cylinder ~(C2) recesses are con-netted through passages 150,151 and ports 152,153 in the power steering unit aye and high pressure hydraulic hoses to oppose in sides of a double acting hydraulic steering cylinder (all not shown). The pressure l(Pl) and pressure 2(P2) recesses are con-netted through passages 154, 155 and port 156 in the power steer in unit aye and high pressure hydraulic hoses to the high pressure ox let of a hydraulic pump driven by an engine tall not shown). The return l(Rl) and return 2(R2) recesses are con-netted together through passage 157 and through passage 158 and port 159 in the power steering unit aye and high pressure hydraulic hoses to the low pressure inlet of the hydraulic pump (all not shown).
The center passage 131 of the power steering unit 127, aye communicates to the drive hole 141 and inner fluid passage-way of the device. The media (lM1) recess of the power steering unit aye communicates to passage 130 and the outer fluid passageway of the device.

I

1 In operation the selective rotation of the input shaft 142 is transformed into axial movement of the slide member 129, aye through a pin-helical groove connection 143 within the limits of motion allowed by the torsion spring connection 144 to the wobble stick and thereafter into direct rotation of the wobble stick 145.
The axial movement of the slide member aye inter connects the recesses aye and passages 130-131 selectively In the turning position shown in drawing 29, passage 130 is con-netted throl7gh the media l(Ml) recess to pressure 2(P2~ and the center passage 131 of the device 127 is connected lo the Solon-don 2.
The fluid from passage 130 travels through holes 132 in plates 133, 134 and 135 and the commutation passages 138 in plate 136 to the seven outer annuls holes 139 in plate 137.
From the outer holes 139 in the plate 137 the fluid communicates through annular channels 37 to some of the openings 34 that are located inside the outer holes 139. The openings 34 extend through plates 137, 136 and 135 to connect with the spiral passages 140 in plate 134~ and through the spiral passages 140 to connect with openings 41, respectively. Openings 41 ox-tend through plates 135, 136 and 137 to open into the gyrator cells of the device 127, aye.
While the outer holes 139 are communicating by openings 34 to openings 41 leading to expanding gyrator cells, fluid from openings 41 leading contracting fluid cells communicates dip neatly with the center passage 131 of the device through the drive hole 141 in the center of the rotor.
In an opposite turn the reverse would be true.
FIGURE 35 is shown in a neutral unturned position.

JO

1 In these hydraulic devices plates 133-137 are brazed together to form a single unitary structure.
In the hydraulic device of FIGURE 29, the fluid ports, the recesses (Pi, Al, Pi, Ml, Of, R2 and C2) and the respective fluid passages there between in the body 127 of the steering unit must be cast and/or machined. These are time and labor consuming manufacturing operations In the alternate device of FIGURE 35, a series of plates 146 simplify the construction of the fluid passages in the device between the port openings and the recesses (Pi, Al/ Pi, Ml, Of, R2 and C2) in the housing aye of the device; this in addition to the series of plates 147 that simplifies the con-struction of the fluid passages connecting the 130 recess, respectively, with the rotor cells.
Each plate of the series of plates 146, 147 is designed for ease of individual manufacture (usually by stamping) and to reduce or to simplify the construction of the remainder of the device. (For example in the device disclosed, the fluid passages 14g and 149 in the housing aye are designed for con-struction in one perpendicular drilling operation from the flat face of the housing aye). The series of plates are then brazed together to form a single unitary structure.
The multi-plate construction of the gyrator porting, plates 147, and of the body of the steering unit, plates 146, greatly reduces the cost of construction while increasing the flexibility of power steering units.
While I have illustrated and described a preferred embodiment of my invention, it will be understood that this is by way of example only and not to be construed as limiting.

Claims (8)

THE EMBODIMENTS OF THE INVENTION IN WHICH AN EXCLUSIVE
PROPERTY OR PRIVILEGE IS CLAIMED ARE DEFINED AS FOLLOWS:

1. In a gerotor hydraulic pressure device having a housing, a rotor with a certain eccentric rotary motion and full revolution commutation between a fluid passage in the housing and a fluid passage in the rotor, the improvement of one of the fluid passage in the housing or the fluid passage in the rotor being laid out in substantially the pattern traced by a given point of the other of the fluid passage in the housing or the fluid passage in the rotor, said pattern substantially following the certain eccentric rotary motion of the rotor, the laid out passage following said pattern facilitating the fluid commutation between the passages.

2. The improved gerotor hydraulic pressure device of Claim 1 wherein the fluid passage laid in substantially said pattern substantially following the certain eccentric rotary motion of the rotor is a ring channel and characterized in that the ring channel is star-shaped, the points of which are directed towards the cells of the gerotor device.

3. In a gerotor hydraulic pressure device having a housing, a rotor with a certain eccentric rotary motion and full revolution commutation between a fluid passage on a surface of the housing with a fluid passage on facing surface of the rotor, the improvement of one of the fluid passage of the housing or the fluid passage of the rotor being laid out substantially in the pattern traced on the surface corres-ponding to said one fluid passage by a given point of the other of the fluid passage of the housing or the fluid passage of the rotor, said pattern substantially following the eccentric rotary motion of the rotor, said laid out passage improving the commutation between the fluid passages.

4. The gerotor hydraulic device of Claim 3 wherein said one fluid passage is laid out in a substantially star shaped pattern.

5. In a gerotor hydraulic pressure device having a housing, a rotor with a certain eccentric rotary motion and full revolution commutation between a fluid passage on a surface of the housing with a fluid passage on facing surface of the rotor, the improvement of the fluid passage of the housing being laid out substantially in the pattern traced on the surface of the housing by a given point of the fluid passage of the rotor, said pattern substantially following the eccentric rotary motion of the rotor, said laid out passage improving the commutation between the fluid passages.

6. The gerotor hydraulic device of Claim 5 wherein said one fluid passage is laid out in a substantially star shaped pattern.

7. In a gerotor hydraulic pressure device having a housing, a rotor with a certain eccentric rotary motion, and full revolution commutation between a fluid passage on a surface of the housing with a generally circular symmetrically shaped fluid passage on a facing surface of the rotor, the improve-ment of the fluid passage of the housing being laid out sub-stantially in the pattern traced by a given point of the generally circular fluid passage of the rotor, said pattern substantially following the eccentric rotary motion of the rotor, said laid out pattern improving the communication between the fluid passages.

8. A gerator hydraulic pressure device as claimed in Claim 1 substantially as herein described and shown in the accompany-in drawings.