US3869231A

US3869231A - Vane type fluid energy translating device

Info

Publication number: US3869231A
Application number: US403125A
Authority: US
Inventors: Cecil E Adams
Original assignee: Abex Corp
Current assignee: Hagglunds Denison Corp
Priority date: 1973-10-03
Filing date: 1973-10-03
Publication date: 1975-03-04
Anticipated expiration: 1992-03-04
Also published as: CA998292A; GB1478347A; DE2438707A1; IT1016930B; IN141700B; FR2246753B1; FR2246753A1

Abstract

A vane type fluid energy translating device has a rotor with a plurality of vane slots each containing a movable vane which traverses the inner surface of a cam ring. Each vane has leading and trailing faces which are nonparallel and when one face is subjected to a higher fluid pressure the other face is acted on by a reaction force between it and the rotor which force has a component that biases the vane outwardly of its rotor slot toward engagement with the cam ring.

Description

United States atent Adams I [451 Mar. 4, 1975 1 "VANE TYPE FLUID ENERGY TRANSLATHNG DEVICE [75] Inventor: Cecil E. Adams, Columbus, Ohio [73] Assignee: Abex Corporation, New York, NY.

[22] Filed: Oct. 3, 1973 [21] Appl. No.: 403,125

[52 U.S. Cl. 418/267, 418/268 [51] Int. Cl. F0lc 1/00, F03c 3/00, F040 1/00 [58] Field of Search 418/249, 267, 268, 260,

[56] References Cited UNITED STATES PATENTS 1,651,336 11/1927 Wissler 418/268 2,278,131 3/1942 Livermore 418/268 2,628,568 2/1953 Rhine 418/268 Farron 418/268 Rosaen 418/268 Primary E.\'aminerJohn J. Vrablik Attorney, Agent, or FirmThomas S. Baker, Jr.; David A. Greenlee 15 Claims, 16 Drawing Figures TAT FORCE A1 PATENTED MAR 4 I975 sumsqgg CL l H I; Q

f I T5 15/ g 5 ROTATION FORCE F ROTATI ON FIGES PATENTEDHAR 41% saw s an ROTAT I ON FIG. 10

FIGH

PATENTEU 4i975 3,869,231

SHEET70F8 FIG. 13

FIG. 12

VANE TYPE FLUID ENERGY TRANSLATING DEVICE BACKGROUND OF THE INVENTION 1. Field of the Invention The instant invention relates to vane type fluid energy translating devices and more particularly to the vane and rotor of such a device.

2. Description of the Prior Art A common type of vane type fluid energy translating device such as a pump includes a rotary member or rotor having a plurality of slots spaced around its periphery and a movable vane positioned in each slot. The other ends of the vanes engage the inner or cam surface of a stator or cam ring which surrounds the rotor. The sides of the rotor and the side edges of each vane are in sliding, sealing engagement with cheek or port plates on opposite sides of the rotor.

The inner surface of the cam ring is con-toured so that the distance between it and the periphery of the rotor varies around the circumference of the rotor. A fluid pumping or intervane space is defined by the rotor periphery, the inner surface of the cam ring, the port plates and adjacent pairs of vanes. As the vanes traverse the cam surface they sequentially pass through an intake or suction zone, a transfer zone, a discharge or exhaust zone and a sealing zone.

In the suction zone, inlet ports in the cheek plates open into the intervane space and the cam surface recedes from the rotor to provide an enlarged pumping space. In the transfer zone, the distance between the cam surface and the rotor remains substantially constant. In the discharge zone, the cam surface approaches the rotor to reduce the volume of the intervane space and exhaust the fluid through outlet ports in the cheek plates. Spacing between the cam surface and the rotor remains substantailly constant in the sealing zone.

Since the distance between the cam surface and the rotor varies around the periphery of the cam surface, each vane must be free to move in and out of its respective slot in the rotor as rotation progresses. Conventionally, vanes and rotor slots are carefully machined to have parallel faces to insure smooth sliding of the vane in the slot with minimum fluid leakage. It is important to the efficient operation of the fluid energy translating device that each vane remains in positive contact with the cam surface but exerts a relatively low force on the surface as the vane traverses it. These devices commonly utilize one or more auxiliary means for biasing the vanes outwardly of their respective rotor slots.

One way of maintaining contact between the vanes and the cam surface is described in the patent to Adams et al., U.S. Pat. No. 2,856,861, issued Oct. 21, 1958. In this vane type fluid energy translating device, the inner end of each vane which is approximately hydraulically balanced in the radial direction is counterbored to receive a coil spring. This spring is disposed in a socket formed in the bottom of the slot which receives the vane. The spring is compressed between the bottom of the slot and the vane and urges the vane outwardly of the slot into contact with the inner surface of the cam ring. The biasing force on the vane can be altered by changing the size or increasing the number of springs placed in each rotor slot.

Another means for assuring that each vane maintains contact with the inner surface of a cam ring is described in the Pat. to Adams et al., U.S. Pat. No. 2,832,293 issued Apr. 29, 1958. In this device, recesses connect the inner end and the outer end of each vane so that both ends of the vane are under the same pressure and they are approximately hydraulically balanced. A groove is provided for conducting fluid under discharge pressure to an inward groove formed in a central opening in the rotor. This groove conducts the fluid under discharge pressure to the inner ends of piston chambers formed in the rotor. These chambers extend radially from the groove to the inner ends of the vane slots and receive radially movable piston pins. The fluid under pressure causes the pins to move radially outward to engage the inner ends of the vanes and urge the vanes into engagement with the cam surface. By changing the size and the number of pins in each rotor slot, the desired force to maintain. the vanes in sealing engagement with the inner surface of the cam ring can be obtained.

Although auxiliary actuators such as springs and piston pins in conjunction with radially balanced vanes assure positive contact between the vanes and'the cam surface, they have also increased the size of the rotor as well as the height and/or thickness of the vanes and the overall size of the fluid energy translating device. They also make the device more complex and increase the cost of the device.

It is desirable to have a fluid energy translating device in which the vanes will be maintained in positive contact at a low force level with the inner surface of the cam ring as the rotor is turned by without using additional actuating members.

SUMMARY OF THE INVENTION The instant invention provides a vane type fluid energy translating device in which each vane and its respective rotor slot cooperate to bias the vane outwardly and into contact with the inner surface of a cam ring. Each vane has leading and trailing faces, one of which has a portion that is nonparallel to the other face. Rotation of the rotor causes each vane to sequentially tra verse intake, transfer, discharge and sealing zones and each vane is subjected to a pressure differential relative to the leading and trailing faces while traversing the transfer and sealing zones.

The pressure differential forces the nonparallel portion of the vane against the rotor slot wall. Since the vane faces are nonparallel, a reaction force is produced having an outward component biasing the vane outwardly of the slot and into engagement with the cam surface.

Accordingly, it is an object of this invention to provide a vane type fluid energy translating device wherein each vane and its respective rotor slot cooperate to bias the vane outwardly of the slot toward engagement with the inner surface of the cam ring without an auxiliary actuating device.

It is a further object of this invention to provide a vane type fluid energy translating device wherein a pressure differential across the vane faces creates an outward force biasing the vane outwardly of the rotor slot.

Other objects of the invention will appear hereinafter, the novel features and combinations being set forth in the claims.

DESCRIPTION OF THE DRAWINGS FIG. 1 is an end elevation of the fluid energy translating device of this invention.

FIG. 2 is an axial section taken along line 22 of FIG. 1.

FIG. 3 is a transverse sectional view taken along line 3-3 of FIG. 2.

FIG. 4 is an enlarged developmental view of approximately 180 of the structure of FIG. 3 showing one embodiment of the invention.

FIG. 5 is similar to FIG. 4, but illustrates a second embodiment of the invention.

FIG. 6 is an enlarged view of one of the vanes shown in FIG. 4.

FIG. 7 is an enlarged view of a portion of the rotor of FIG. 4 showing one of the vane slots.

FIG. 8 is an enlarged view of a portion of FIG. 4 showing a vane in extended position 3 and illustrating the operation of the invention.

FIG. 9 is similar to FIG. 8, but showing the vane in retracted position 6.

FIG. 10 is an enlarged view of one of the vanes shown in FIG. 5.

FIG. 11 is an enlarged view of a portion of the rotor of FIG. 5 showing one of the vane slots.

FIG. 12 is an enlarged view of a portion of FIG. 5 showing a vane in retracted position 6 and illustrating the operation of the invention.

FIG. 13 is an enlarged view of a portion of FIG. 5 showing a vane in extended position 3.

FIG. 14 illustrates a double lip vane which is a third embodiment of the instant invention.

FIG. 15 illustrates a slot in which the vane of FIG. 14 operates.

FIG. 16 shows the vane of FIG. 14 in the slot of FIG. 15 and illustrates the operation of the third embodiment of the invention.

DETAILED DESCRIPTION The invention described and claimed herein is applicable to a vane type fluid energy translating device. This device constitutes a pump if the rotor is driven by a prime mover or a motor if the rotor is caused to rotate because of a greater pressure at the inlet port than at the outlet port. To facilitate the description, the device will-be referred to hereinafter as a pump.

A pump 10 which incorporates the instant invention can be seen in FIGS. I3 and has a housing formed by a body casting l1 and an end cap 12. A recessed shoulder 13 on end cap 12 is telescopically received in one end of casting 11 and is sealed by an O-ring 14. Casting l1 and end cap 12 are connected by fastening means such as bolts, not shown.

End cap 12 has an opening 15 to receive a shaft 16. Shaft 16 is supported in end cap 12 by a ball bearing 17 which is located in opening 15 between a shoulder 18 and a snap ring 19 which prevents axial movement of bearing 17. A seal 20 prevents oil leakage along shaft 16 to the outside of pump 10. shaft I6 is supported at its inner end by a needle bearing 22 which is received in an opening 23 in casting 11.

End cap 12 supports a front cheek or port plate 25 which has a smooth, flat inner surface 26 that bears against one side 27 of an annular cam ring or stator 28. A rear port plate 29 has a smooth, flat inner surface 30 which bears against the opposite side 31 of cam ring 28.

Cam ring 28 is supported in an annular rib 38 in casting 11 and is clamped between

port plates

25, 29 by the outlet pressure in a chamber 24.

Fluid is supplied to pump 10 through a fluid intake passageway 33 which extends into casting 11 and communicates with a pair of

annular channels

34, 35 that supply fluid to

inlet ports

36, 36 and.

undervane inlet ports

37, 37 in each of the

port plates

25, 29.

The cam ring 28 surrounds a rotor 39 which is splined at 40 to shaft 16. Formed in the rotor 39 are a plurality of slots 41, each of which receives a vane 42. Each vane'42 has an outer end 43 with a slanted outer surface 46 behind an apex 47 which engages the inner or cam surface 48 of cam ring 28.

Cam surface 48 is contoured to provide a symmetrical pump construction. For each of shaft rotation, each vane successively traverses suction, transfer, discharge and sealing zones in the direction of rotation shown in FIGS. 3, 4 and 5. Cam surface 48 recedes from the rotor 39 in the suction zone forming a suction ramp 51 and surface 48 is at its greatest distance from the rotor 39 at the beginning of its major diameter 52 in the transfer zone. It is common to provide a slight inward slope of major diameter 52. The cam surface 48 moves inwardly toward rotor 39 across the discharge zone and has an inwardly approaching discharge ramp 53. Cam surface 48 is closest to the rotor 39 at its minor diameter 54 across the sealing zone.

Inlet ports 36 provide fluid to the intervane space 5 defined by rotor 39, cam surface 48 and

port plates

25, 29 throughout the full span of suction ramp'SI. Undervane inlet ports 37 supply fluid at suction pressure to the inner end 49 of each vane 42. This fluid also flows up opening 44 to help fill the intervane space 50. Outlet ports 56 discharge fluid from the intervane space 50 throughout the span of discharge ramp 53. This fluid flows through cored passages (not shown) into outlet chamber 24 and through fluid outlet passageway 21. Together, inlet ports 36 and suction ramp 51 define the suction zone while outlet ports 56 and discharge ramp 53 define the discharge zone.

The operation of pump 10 can be seen by referring to FIG. 4. A prime mover (not shown) rotates shaft 16 and rotor 39. Thus vanes 42 traverse cam surface 48 and move in and out of rotor slots 41. Each vane 42 successively traverses the suction zone and the intervane space 50 is filled with fluid from inlet port 36. The

vanes

42, 42 which define the ends of the intervane space 50 next move the fluid across the transfer zone. At theend of this zone fluid in the intervane space 50 is gradually exposed to fluid in the outlet port 56 by means of a bleed slot 57. The front vane 42 then traverses the discharge zone and rear vane 42 seals the intervane space 50 from the suction zone. As front vane 42 traverses the discharge zone, fluid under pressure is forced out of the intervane space 50 and into outlet port 56. After the discharge zone, the front vane 42 traverses the sealing zone. The front vane 42 of intervane space 50 prepares to enter the suction zone when the rear vane 42 has moved out of the discharge zone and sealed the intervane space 50 from that zone.

During the time the vanes 42 are traversing the suction zone and the discharge zone, the hydraulic pressure is approximately equal at each of the vane ends 43, 49, i.e., the vanes 42 are hydraulically balanced. In these zones, centrifugal force tends to bias vane 42 outwardly of its rotor slot 41 and into engagement with cam surface 48. It is necessary to have an additional force to bias the vanes 42 outwardly of their slots 41 as they traverse the transfer zone and the sealing zones since the radial forces resulting from fluid pressure are not equal on both ends 43, 49 of the vanes 42 in these zones.

The preferred embodiment of the vane and rotor of this invention is shown in FIGS. 1-4 and 6-9. As shown in FIG. 6, vane 42 is generally rectangular in shape with a flat leading face 58 joined to slightly beveled surface 59 along line 65. The trailing face has two

flat surfaces

61, 62 which are parallel to the leading face 58 and which are joined by a pair of inwardly

angled surfaces

63, 64 along

lines

76, 69 respectively. An orifice 68 at the intersection of

surfaces

63, 64 provides restricted fluid communication between leading face 58 and trailing face 60.

Outer end 43 of vane 42 has a chamfered surface 67 which joins the slanted outer surface 46. The apex 47 which engages cam surface 48 is at the joint between end surfaces 46, 67.

FIG. 7 illustrates the rotor slot 41 in which vane 42 is carried. Slot 41 is defined by a pair of generally

parallel walls

70, 71. The

outside corners

72, 73 of

walls

70, 71 are rounded slightly. A drilled passage 44 connects the inner end 45 of slot 41 to the outer surface of rotor 39. Passages 44 assure continuous communication between outer surface 46 and inner end 49 of vane 42.

The operation of the preferred embodiment of the vane and rotor ofthe instant invention which biases the vane into engagement with the cam surface in the transfer and sealing zones will next be described with reference to FIGS. 8 and 9.

'FIG. 8 shows how vane 42 and rotor slot 41 cooperate to bias vane 42 towards cam surface 48 as vane 42 traverses the transfer zone. The vane is in position 3 in FIG. 4. Here, vane 42 if fully extended from slot 41, and is beginning to traverse the transfer zone. In this position, inner end 49, outer surface 46 and the portion of

surfaces

61, 63 on the trailing face 60 that overhang rotor 39 are interconnected by passage 44 and are exposed to suction pressure. In the drawings, suction pressure is designated S and discharge pressure is designated P. Chamfered surface 67 and leading face 58 are exposed to discharge pressure P. Inner end 49 and the combined surfaces 46 and 67 of outer end 43 of vane 42 have the same area, but since surface 67 on outer end 43 is acted upon by the discharge pressure P and no such pressure acts upon inner end 49, a net inward force A tends to move vane 42 inwardly away from cam surface 48. If surface 67 has dimensions of 0.01 inch wide by 1.9 inches long and a net fluid pressure of 3,000 psi acts on surface 67 then inward force A acting on outer end 43 of vane 42 will be (area of 0.01 inch X 1.9 inches multiplied by 3,000 psi) which is 57 pounds.

An outward component of force acting on vane 42 will now be described. In vane 42 and rotor 39 of the instant invention, the discharge pressure P which acts on leading face 58 results in a force B which is perpendicular to this face. If it is assumed that the dimensions of leading face 58 that are subjected to discharge pressure P are 0.5 inches high by l.9 inches long and the pressure is 3,000 psi, then force B will be (area of 0.5 inches X 1.9 inches multiplied by 3,000 psi) which is about 2,850 pounds. Force B tilts vane 42 rearwardly in slot 41 such that angled surface 63 of trailing face 60 surface 63 perpendicular to surface 63. Since surface 63 and face 58 are not parallel, force C does not act parallel to force B. Resolving force C produces a radial force component D which biases vane 42 outwardly of slot 4]. Torque forces on vane 42 can be ignored if the radial vane overhang beyond the rotor slot corner 72 is approximately equal in radial distance to the distance from slot corner 72 to the line 65 at the intersecting vane surfaces 58, 59.

The magnitude of force D is determined in the following way. Force D will equal the value of force B times the tangent of the angular difference between leading face 58 and angled surface 63. In the instant invention, it has been found that, if surface 63 is angled with respect to surface 61 and face 58 by 2, an acceptable value of force D will be obtained. Force D will be the value of force B which is 2,850 pounds multiplied by the tangent of 2 (0.03492) which equals 100 pounds.

It should be noted that the lines of force illustrated in FIG. 8 are intended to be illustrative and are not intended to be to the proper scale.

Inward acting force A equals 57 pounds and outward acting force D equals 100 pounds. The difference is a net force of 43 pounds biasing vane 42 outward into engagement with cam surface 48. Centrifugal force also acts to urge vane 42 outward. Force D and the centrifugal force are resisted by cam surface 48. The net outward force of 43 pounds will allow for wear of apex 47 and outer surface 46 which could increase the area of surface 67 and also the value of force A.

The value of force D can be increased or decreased simply by increasing or decreasing the angle between leading face 58 and surface 63 on trailing face 60. Force D responds only to the angularity described and is not affected by the vane tilting in the slot 41.

Force A which tends to move vane 42 inward is directly proportional to the pressure differential existing between the leading and trailing faces 58, 60 for any dimension of surface 67. Likewise, force D, which overcomes and exceeds force A, is also directly proportional to the same pressure differential. Consequently, there is always a net force tending to bias vane 42 outwardly of slot 41 as it traverses the transfer zone of the pump. This is true even if the rotor width and associated vane width are changed because the forces A and D will both change in direct proportion to the vane width dimension.

The values of forces A and D are not a function of speed or centrifugal force so there will be a net outward force on vane 42 adequate for it to lightly track the cam surface 48 in the transfer Zone under all conditions of speed and pressure.

The vane 42 is lubricated as it traverses the transfer zone in the following way. When vane 42 is tilted backwards in rotor slot 41 and supported by corner 72, a clearance gap 74 is created between vane face 58 and rotor slot wall 71. A small amount of fluid under pressure can then flow through gap 74, orifice 68 and into a pocket formed at the intersection of

angled surfaces

63, 64 in the trailing face 60. The orifice 68 and pocket 75 lubricate the vane and slot bearing surfaces with fluid under a positive pressure and thus reduce wear on vane surface 63 and slot corner 72 as vane 42 moves relative to slot 41 while traversing cam surface 48. Because the small amount of fluid flow that passes through orifice 68 leaks in turn through the small clearances between vane 42, rotor slot 41 and

port plates

25, 28 only a small back pressure is retained in pocket 75 and the forces described are not materially affected. This fluid escapes into the suction area S.

The operation of vane 42 in slot 41 while traversing the sealing zone in retracted position 6 of FIG. 4 is illustrated in FIG. 9. At this position discharge pressure P acts on slanted outer surface 46 and inner end 49 of vane 42 through rotor passage 44. Outer end vane surface 67 and leading face 58 are exposed to suction pressure S.

Since the vane is retracted, the

parallel surfaces

61, 62 engage

rotor slot'side walls

70, 71 respectively and so there is no mechanical radial force component biasing vane 42 outwardly.

Since inner end 49 of vane 42 is acted upon by discharge pressure p and the same pressure acts on surface 46 which is only a portion of outer end 43, vane 42 is radially unbalanced by a hydraulic force F. The value of force F is determined by the area of surface 67 times the difference between discharge P and suction S pressures. If chamfered surface 67 has dimensions of 0.0l inch wide by 1.9 inches long and the pressure difference is 3,000 psi, force F will be 57 pounds (area of 0.01 inch X 1.9 inches X 3,000 psi). as may be expected, this is the same value as force A, but acting outwardly because of the transposition of pressures P and S.

A cycle of operation for the preferred embodiment can best be seen by referring to FIG. 4. The pump zones are numbered in FIG. 4 for clarity. Rotation of the rotor expands the intervane space 50 as the vane traverses the suction zone from position 1 past position 2, and fluid is drawn into the intervane space 50 through the inlet port. The centrifugal force acting on the vanes as they move through the suction zone is sufficient to bias the vanes into engagement with the cam surface since the inner and outer end of each vane are each exposed to the same suction pressure S which causes the hydraulic forces on each of the ends to be balanced.

As a vane reaches position 3 and begins to traverse the transfer zone, the vane is subjected to suction pressure S on one side and discharge pressure P on the other side and the pressure differential tilts the vane in its slot and a reaction force which has an outward component biases the vane outwardly and into engagement with the cam surface as previously described.

As a vane traverses the discharge zone from position 4 to position 6, the volumetric capacity of the intervane space 50 is decreased and fluid is forced out through the outlet port. As a vane traverses the discharge zone, it is biased into engagement with the cam surface, primarily by centrifugal force. Also, a small hydraulic biasing force is available to assist tracking. This force results from fluid under vane 42 being displaced and forced upward through passage 44 while vane 42 moves inwardly and simultaneously restricts flow into the passage 44.

As the vane traverses the sealing zone from position 6 to position 1, the radial force necessary to bias the vane outwardly into engagement with the cam surface is obtained by the pressure differential between the inner and outer ends of the vane as previously described.

The aforementioned cycle repeats through the next 180 of rotation which completes one revolution of the rotor and vanes.

A second embodiment of the vane and rotor of the invention is illustrated in FIGS. 5 and 10 through 13. In this embodiment, the vane and rotor slot cooperate to produce a component of force tending to bias the vane outward of the slot as the vane traverses the sealing zone. A pressure differential between the inner and outer ends of the vane biases the vane outward of the slot as it traverses the transfer zone.

In the second embodiment, a vane 142 has an inner end 143 which comprises two

angled surfaces

144, 145 which are joined by a third surface 146. The outer end 147 of vane 142 comprises a slanted surface 148 on one side of an apex 149 and a notched corner 150 on the opposite side of apex 149. The purpose of a notched corner instead ofa chamfer is to keep the apex at about the same distance from the flat trailing face 151 as the apex wears. The leading face 152 comprises a surface 153 which is angled approximately 5 with respect to trailing face 151, which surface 153 joins a surface 154 which is parallel to trailing face 151. Surface 154 joins an angled surface 155 which joins another surface 156. Surface 156 is parallel to trailing face 151 and the greatest width of vane 142 is between surface 156 and trailing face 151. Of equal width is the vane at the outer end between face 151 and the top of surface 153. A line 157 is formed where

surfaces

155, 156 are joined. Vane 142 pivots about line 157 as described below.

Rotor 139 comprises a plurality of slots 141 each of and the surface of rotor 139. Fluid from undervane inlet port 170 flows through passage 163 to help fill the intervane space.

A channel 164 breaks into rotor slot face 160 and extends axially across the rotor width. Opening cont nects channel 164 to the space at the outer surface of rotor 139, but at the trailing side of vane 142, as contrasted to opening 163 which opens at the leading side of vane 142.

Channel 164 serves a dual purpose. First, it allows discharge pressure fluid behind vane 142 during one part of the cycle to extend over a large portion of trailing face 151. Secondly, it receives inlet fluid from an auxiliary suction port 171 in the suction zone and passes fluid up passage 165 to help fill the intervane space.

Slot face 161 has an angled surface 166 at the top thereof. Surface 166 may form an angle of approximately 5 with respect to face 161.

The operation of the second embodiment of the vane and rotor as the vane traverses the sealing zone can be seen in FIG. 12. The position of vane 142 with respect to earn surface 167 in the sealing zone can also be seen in FIG. 5 where it is position 6. In this position, discharge pressure P is applied to notched corner 150 and to a substantial portion of trailing face 151 through opening 165 and channel 164. Surfaces I53, 156 on leading face 152 and surface 148 on outer end 147 and inner end 143 of vane 142 are exposed to suction pressure S.

-A hydraulic force A acts to urge vane 142 inward of rotor slot 141. The value of force A can be determined in the following way. If notched corner 150 behind apex 149 has dimensions of 0.01 inch wide and 1.9 inches long and a pressure differential of 3,000 psi exists between inner and

outer ends

143, 147 respectively, vane 142 will be hydraulically unbalanced inwardly by 57 pounds (area of 0.01 inch times 1.9 inches multiplied by 3,000 psi), which is the value of force A.

When discharge pressure P is applied to trailing face 151, vane 142 will tilt forwardly in slot 141 thrusting angled vane surface 153 against angled slot surface 166 with line 157 as a fulcrum. If the discharge pressure P is applied to the upper 0.235 inch of surface 151 and surface 151 is 1.9 inches long, a force B tilting the vane 142 forwardly will be (area of 1.9 inches 0.235 inch multiplied by the pressure differential 3,000 psi) which equals 1,340 pounds.

The determination of the value of force E which tends to bias vane 142 outward of slot 141 is described in the following: If by way of example the center of force Bis 0.192 inch above fulcrum line 157 and the center of force C between angled vane surface 153 and angled slot surface 166 is 0.235 inch above line 157, then the value of force C which tends to thrust surface 153 against surface 166 will be 1,340 pounds multiplied by 0.192 inch by 0.238 inch) which equals approximately 1,081 pounds.

Force B acts perpendicular to vane face 151 and force C is parallel to force B. A reaction force D between

surfaces

153, 166 resists force C and is perpendicular to vane surface 153. Vane surfaces 151 and 153 are not parallel and force D has a component, force E, which will act to bias vane 142 outward of slot 141. The value of outward force E in this example will be force C multiplied by the tangent of the angular difference between vane faces 153, 151. If the angular difference is the tangent of which is 0.08749, then force E equals (1,081 pounds times 0.08749) which is 95 pounds. By subtracting inward force A of 57 pounds from outward force E of 95 pounds, there is a net outward force on vane 142 of 38 pounds which biases vane 142 into engagement with cam surface 167.

The operation of vane 142 and rotor 139 of the instant invention when vane 142 traverses the transfer zone is illustrated in FIG. 13. The position of vane 142 with respect to cam surface 167 can also be seen in FIG. 5, where it is in position 3. In this-position,

parallel surfaces

151, 156 are guided between the parallel faces 160, 161 of rotor slot 141. The width of vane 142 is greatest between

surfaces

151, 156 and vane 142 cannot tilt relative to slot 141. Since there is no angularity involved between vane faces 151 and 156, there is no radial force component acting upon the vane as there was at the sealing zone.

In the transfer zone, discharge pressure P acts on

surfaces

153, 154 and 155 ofleading face 152, surface 148 of outer end 147 and inner end 143 of vane 142. Trailing face 151 and notched corner 150 behind apex 149 are exposed to suction pressure S. Since the full area of inner end 143 of vane 142 is exposed to discharge pressure P, but only slanted surface 148 of outer end 147 is exposed to this pressure, vane 142 will be hydraulically unbalanced and biased outward of slot 141.

An example of the force 11 which tends to bias vane 142 outward is as follows: Assuming that notched corher has dimensions of 0.01 inch wide by 1.9 inches long, and if the pressure differential is 3,000 psi, then force H will be (area of 0.01 inch X 1.9 inches multiplied .by 3,000 psi) 57 pounds. This force can be changed by moving apex 149 forward or backwards to change the area of unbalance.

The major difference between the structure of the preferred embodiment and the structure of the second embodiment is that the rotor and vanes of the former cooperate to form a mechanical reaction which has an outward component of force on the vanes as they traverse the transfer zone, whereas, the rotor and vanes of the latter structure are operative to provide a reaction with an outward component of force as the vanes traverse the sealing zone. The structure of the preferred embodiment is hydraulically unbalanced by a force tending to bias the vanes outwardly of the rotor as they traverse the sealing zone, whereas the structure of the second embodiment is hydraulically unbalanced by a force tending to bias the vanes outwardly of the rotor as they traverse the transfer zone.

A third embodiment of a vane and rotor is shown in FIGS. 14 through 16. The vane in this structure has two lips and the vane and rotor slot cooperate to produce a reaction force which has a component of force which biases the vane outward from the slot as the vane traverses both the transfer zone and the sealing zone. As described above, the structure of one of the previous embodiments was operative to provide a reaction with an outward component of force in the transfer zone and the structure of the other embodiment was operative to provide a reaction with an outward component of force in the sealing zone, but neither of the previous embodiments provided a reaction with an outward component of force in both zones. The instant embodiment is particularly desirable for use in a fluid energy translating device which will be used as both a pump and a motor. The vane is symmetrical and the rotor slot is symmetrical; consequently, the structure is operative for either direction of rotation of the rotor.

FIG. 14 illustrates the vane 242 of the instant em bodiment. One face 243 has two

angled surfaces

244, 245 joined along line 246 and a third angled surface 247 joined to surface 245 along line 248. The other face 253 has two

angled surfaces

254, 255 joined along line 256, and a third angled surface 257 joined to surface 255 along line 258. A top groove 249 and end grooves 250 connect the outer end 251 and the inner end 252 of the vane.

Faces

243, 253 are symmetrical and the greatest width of vane 242 is between

lines

248, 258 and

corners

260, 261. The vane width at these two places is the same.

Corners

260, 261 may be slightly chamfered as shown in FIG. 14.

Rotor slot 241 which receives vane 242 of the instant embodiment is illustrated in FIG. 15. Slot 241 is formed by a pair of

parallel walls

263, 264 with

chamfered corners

265, 266 at the circumference of rotor 239.

Channels

267, 268 break into the faces. 263, 264 respectively and extend across the width of rotor 239.

Radial grooves

269, 270

connect channels

267, 268 respectively to the outer surface of rotor 239. Slot 241 has a relief 271 at its inner end.

A counterbore 272 extends inwardly from relief 271. Another counterbore 273 is located in inner end 252 of vane 242. The purpose of

counterbore

272, 273 is to receive a spring 274 which urges vane 242 outwardly of slot 241. This spring is only necessary if the vane and rotor of the instant embodiment are to be used in a motor. When the device acts as a motor, fluid under pressure acts against the vanes which drive the rotor and the rotor can only be started if the vanes are engaging the cam surface 240. It the device is acting as a pump, the rotor is driven and centrifugal force will move the vanes 242 outwardly when the device is started.

Although a spring is commonly used to bias the vane outwardly of the slot when the fluid translating device is being used as a motor, it is necessary to have another means for biasing the vane away from the rotor as the spring lacks the necessary force to adequately bias the vane outwardly when the vane is subjected to the pressure differential in the transfer and sealing zones.

The operation of vane 242 in rotor slot 241 is illustrated in FIG. 16. Since vane 242 is symmetrical as is slot 241, vane 242 is free to tilt in either direction when traversing the transfer or sealing zones depending on which side of it is acted upon by higher pressure. In FIG. 16, the high pressure H acts on

surfaces

254, 255 of face 243 as it would if vane 242 were traversing the sealing zone while the low pressure L acts on face 243. This pressure over

surfaces

254, 255 results in force K perpendicular to the center line of vane 242. Vane 242 is tilted in slot 241 by the high pressure H such that surface 244 is urged against vane slot corner 266. A reaction occurs between surface 244 and corner 266. This reaction, force N is perpendicular to surface 244. Force N has a component, force M, which acts radially outward to bias vane 242 outward of rotor slot 241.

When the direction of the pressures H and L are reversed from that shown in FIG. 16, as when vane 242 traverses the transfer zone, the vane will tilt in the opposite. direction with the reaction occurring between surface 253 and vane slot corner 265. A reaction force with an outward component will again act on the vanes.

The instant invention provides a vane and rotor slot configuration which cooperate to bias the vane outwardly of the rotor when the vane is subjected to a pressure differential in the transfer and sealing zones. Further, the vane and rotor of the instant invention resist the forces tending to bias the vane inward as the vane traverses these zones and keeps the vane biased toward engagement with the cam surface.

It should be noted that in each embodiment a portion of the vane near its inner end has a thickness that constitutes a close fitting, but slip fit between the vane and the rotor slot. This allows for radial vane movement relative to the slot but also seals discharge fluid from suction fluid between the inner and outer ends of the vane and prevents excessive leakage between a vane face and a rotor slot face. Provision is further made to maintain this sealing action and still allow the vanes to tilt relative to the slot in certain zones. Obviously, those skilled in the art may make various changes in the details and arrangements of parts without departing from the spirit and scope of the invention as it is defined by the claims hereto appended. Applicant, therefore, wishes not to be restricted to the precise construction herein disclosed.

Having thus described and shown in the embodiment of the invention, what is desired to secure by Letters Patent of the United States is:

1. A vane type fluid energy translating device comprising: a stator; a rotor; a cam surface formed on the stator; a plurality of vane slots formed in the rotor; a

vane positioned in each vane slot for movement relative thereto and having a leading face, a trailing face, an inner end within the vane slot and an outer sealing lip engageable with the cam surface on the outer end thereof; wherein rotation of the rotor causes each vane to sequentially traverse intake, transfer, exhaust and sealing zones; each vane being subjected to a fluid at high pressure and a fluid at low pressure creating a pressure differential between the leading and trailing faces while traversing the transfer and sealing zones; said pressure differential in at least one of said zones creating a first force on one vane face thrusting each vane against the vane slot as the vane traverses said zone, said fluid at high pressure creating a second force on the outer end of the vane tending to bias the vane into its slot, means connecting the entire inner end of said vane to fluid at low pressure in said one zone; and cooperating means on each vane and the vane slot for effecting a mechanical reaction force opposing said first force which mechanical reaction force has a com ponent greater than said second force biasing the vane outwardly of its slot and into engagement with the cam surface.

' 2. In a vane type fluid energy translating device having a stator member; a rotor member; a cam surface formed on one of the members; a plurality of vane slots formed on the other member; a vane located in each slot for movement relative thereto and having a leading face, a trailing face, an inner end, an outer end and an outer sealing lip formed on the outer end engageable with the cam surface; wherein rotation'of the rotor member causes each vane to sequentially traverse intake, transfer, exhaust and sealing zones; each vane being subject to a fluid at high pressure and a fluid at low pressure creating a pressure differential between the faces while traversing the transfer and sealing zones; said pressure differential in at least one of said zones creating a first force on one vane face, thrusting each vane against the vane slot as the vane traverses said zone; said fluid at high pressure creating a second force on the outer end of the vane tending to bias the vane into its slot, the improvement comprising cooperating means on each vane and the vane slot for effecting a mechanical reaction force opposing said first force which has a mechanical portion of the vane slot, and said connecting means connects the entire inner end and a portion of the outer end of the vane to fluid at low pressure.

3. A vane type fluid energy translating device as recited in claim 2; wherein said cooperating means includes a first surface on the leading face of the vane and a second surface on the trailing face of the vane which surfaces are nonparallel, fluid at high pressure acts on one of said first or said second surfaces to create said first force and said mechanical reaction force is between the other of said surfaces and a part of the vane slot.

4. A vane type fluid energy translating device as recited in claim 3; including means for providing fluid communication between the entire.inner end and a major portion of the outer end of each vane to substantially balance the forces on the inner and outer ends but provide a net hydraulic force which biases each vane outwardly as it traverses the other of said zones.

5. A vane type fluid energy translating device as recited in claim 2; wherein said cooperating means includes a first surface on the leading face of the vane and a second surface on the trailing face of the vane, which surfaces are nonparallel, said pressure differential comprising the net difference of pressure between a fluid at high pressure and fluid at low pressure, the fluid at high pressure acts on said second surface and said first force causes said vane to tilt forwardly in said vane slot, said mechanical reaction force is between the first surface and a surface portion of the vane slot, and said connecting means connects the entire inner end and a portion of the outer end of the vane to fluid at low pressure.

6. A vane type fluid energy translating device as recited in claim 5; wherein said slot is formed with walls, substantial portions of which are parallel and said slot surface portion is angled with respect to said substantially parallel walls.

7. A vane type fluid energy translating device as recited in claim 6; wherein the entire inner end of the vane is exposed to the high pressure fluid and a portion of the outer end of the vane is exposed to the low pressure fluid as the vane traverses the transfer zone to hydraulically unbalance the vane and bias it outwardly of its vane slot.

8. A vane type fluid energy translating device as recited in claim 2; wherein said cooperating means includes a first surface on the leading face of the vane and a second surface on the trailing face of the vane which surfaces are nonparallel, said pressure differential having a fluid at low pressure and a fluid at high pressure said fluid at high pressure acting on the first surface, and said first force causes said vane to tilt rearwardly in said vane slot, said mechanical reaction is between the second surface of said vane and a portion of the vane slot and, the inner end and the outer end of the vane are in fluid communication.

9. A vane type fluid energy translating device as recited in claim 8; wherein said slot is formed with substantially parallel walls and said slot portion which reacts with said second surface on the trailing face is a corner at the top of one of said parallel walls.

10. A vane type fluid energy translating device as recited in claim 8; including an aperture in said vane which provides fluid communication between the leading face and the trailing face for lubricating said second surface and said slot portion.

11. A vane type fluid energy translating device as recited in claim 10; wherein the entire inner end of the vane is exposed to the high pressure fluid and a portion of the outer end of the vane is exposed to the low pressure fluid as the vane traverses the sealing zone to hydraulically unbalance the vane and bias it outwardly of its vane slot.

12. A vane type fluid energy translating device having a stator member; a rotor member; a cam surface on one of the members; a plurality of vane slots formed on the other member; a vane located in each slot for movement relative thereto and having a leading face, a trailing face, an inner end and an outer end and a pair of sealing lips on its outer end alternatively engageable with the cam surface; wherein rotation of the rotor member causes each vane to sequentially traverse intake, transfer, exhaust and sealing zones; each vane being subjected to a fluid at high pressure and a fluid at low pressure creating a pressure differential between the leading and trailing faces while traversing the transfer and sealing zones; said pressure differential creating a first force on one vane face thrusting each vane against the vane slot as the vane traverses either of the zones; said fluid at high pressure creating a second force on the outer end of the vane tending to bias the vane into its slot; the improvement comprising cooperating means on each vane and the vane slot for effecting a mechanical reaction force opposing said first force which has a mechanical force component greater than said second force biasing the vane outwardly of its slots and into engagement with the cam surface; wherein the cooperating means includes a pair of surfaces which form angles on the leading and trailing faces of the vane, the first force acting on the one vane face causes the vane to tilt about the apex formed by the pair of surfaces on the other face, and means connecting the entire inner end of the vane to fluid at low pressure when the vane traverses the transfer and sealing zones.

13. A vane type fluid energy translating device as recited in claim 12; wherein the inner end and a portion of the outer end are in fluid communication with the fluid at low pressure, and the vane tilts about the apex formed by the pair of surfaces on the face exposed to the fluid at low pressure.

14. A vane type fluid energy translating device as recited in claim 13; wherein the cooperating means includes a pair of parallel side surfaces which define each slot and the leading and trailing faces of each vane are symmetrical.

15. In a vane type fluid energy translating device having a stator member; a rotor member; a cam surface formed on one of the members; a plurality of vane supports formed on the other member; a vane located in each support for movement relative thereto and having a leading face; a trailing face, an inner end within said support and an outer end with a sealing lip engageable with the cam surface; wherein rotation of the rotor member causes each vane to sequentially traverse in take, transfer, exhaust and sealing zones; each vane being subjected to a fluid at high pressure and a fluid at low pressure creating a pressure differential between the faces while traversing the transfer and sealing zones; the improvement comprising said pressure differential in at least one of said zones creating a first force acting perpendicular to one vane face thrusting each vane against its support as the vane traverses said zone; a mechanical reaction force between the other vane face and said vane support and acting perpendicular to the other vane face; means connecting said entire inner end of said vane to the fluid at low pressure while traversing said one zone and a portion of the outer end of said vane is subjected to the fluid at high pressure such that said vane is acted on by an unbalanced hydraulic force biasing said vane inward of its support; wherein said mechanical reaction force has a radial component of force greater than said unbalanced hydraulic force and said mechanical reaction force component biases the vane outwardly of its support and into engagement with the cam surface.

UNITED STATES PATENT OFFHJE CERTIFICATE OF CORRECTION PATENT NO. 3 869 231 DATED 1 I March 4 1975 INVENTOR(S) Cecil E. Adams It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

In Claim 2, column 12, line 45 delete "portion of the vane slot"; before the comma, insert force component greater than said second force biasing the vane outwardly of its slot and into engagement with the cam surface said component and centrifugal force being the sole outward acting actuating means for the vane Line 46, delete "said connecting"; after "means", add for change "connects" to connecting Line 47, after "end" (first occurrence) delete "and a portion of the outer end"; after "to", insert the Line 48,

after "pressure" and before the period, insert when said vane is in said one zone Signed and Scaled this twenty-third 1} of March 1 9 76 [SEAL] AIICSI.

RUTH C. MASON C. MARSHALL DANN Arresting Offic (ommissiumr oflatents and Trademarks

Claims

1. A vane type fluid energy translating device comprising: a stator; a rotor; a cam surface formed on the stator; a plurality of vane slots formed in the rotor; a vane positioned in each vane slot for movement relative thereto and having a leading face, a trailing face, an inner end within the vane slot and an outer sealing lip engageable with the cam surface on the outer end thereof; wherein rotation of the rotor causes each vane to sequentially traverse intake, transfer, exhaust and sealing zones; each vane being subjected to a fluid at high pressure and a fluid at low pressure creating a pressure differential between the leading and trailing faces while traversing the transfer and sealing zones; said pressure differential in at least one of said zones creating a first force on one vane face thrusting each vane against the vane slot as the vane traverses said zone, said fluid at high pressure creating a second force on the outer end of the vane tending to bias the vane into its slot, means connecting the entire inner end of said vane to fluid at low pressure in said one Zone; and cooperating means on each vane and the vane slot for effecting a mechanical reaction force opposing said first force which mechanical reaction force has a component greater than said second force biasing the vane outwardly of its slot and into engagement with the cam surface.

2. In a vane type fluid energy translating device having a stator member; a rotor member; a cam surface formed on one of the members; a plurality of vane slots formed on the other member; a vane located in each slot for movement relative thereto and having a leading face, a trailing face, an inner end, an outer end and an outer sealing lip formed on the outer end engageable with the cam surface; wherein rotation of the rotor member causes each vane to sequentially traverse intake, transfer, exhaust and sealing zones; each vane being subject to a fluid at high pressure and a fluid at low pressure creating a pressure differential between the faces while traversing the transfer and sealing zones; said pressure differential in at least one of said zones creating a first force on one vane face, thrusting each vane against the vane slot as the vane traverses said zone; said fluid at high pressure creating a second force on the outer end of the vane tending to bias the vane into its slot, the improvement comprising cooperating means on each vane and the vane slot for effecting a mechanical reaction force opposing said first force which has a mechanical portion of the vane slot, and said connecting means connects the entire inner end and a portion of the outer end of the vane to fluid at low pressure.

4. A vane type fluid energy translating device as recited in claim 3; including means for providing fluid communication between the entire inner end and a major portion of the outer end of each vane to substantially balance the forces on the inner and outer ends but provide a net hydraulic force which biases each vane outwardly as it traverses the other of said zones.

15. In a vane type fluid energy translating device having a stator member; a rotor member; a cam surface formed on one of the members; a plurality of vane supports formed on the other member; a vane located in each support for movement relative thereto and having a leading face; a trailing face, an inner end within said support and an outer end with a sealing lip engageable with the cam surface; wherein rotation of the rotor member causes each vane to sequentially traverse intake, transfer, exhaust and sealing zones; each vane being subjected to a fluid at high pressure and a fluid at Low pressure creating a pressure differential between the faces while traversing the transfer and sealing zones; the improvement comprising said pressure differential in at least one of said zones creating a first force acting perpendicular to one vane face thrusting each vane against its support as the vane traverses said zone; a mechanical reaction force between the other vane face and said vane support and acting perpendicular to the other vane face; means connecting said entire inner end of said vane to the fluid at low pressure while traversing said one zone and a portion of the outer end of said vane is subjected to the fluid at high pressure such that said vane is acted on by an unbalanced hydraulic force biasing said vane inward of its support; wherein said mechanical reaction force has a radial component of force greater than said unbalanced hydraulic force and said mechanical reaction force component biases the vane outwardly of its support and into engagement with the cam surface.