United States Patent 3714969

An improved valve assembly has one inlet and two outlets. The valve is operable to sequentially provide a fluid flow path first between the inlet and one outlet and next between the inlet and both outlets. Utilization of the valve assembly for a rotary vane type air motor driven hoist is described as a preferred embodiment.

Application Number:
Publication Date:
Filing Date:
Primary Class:
Other Classes:
137/596, 418/268
International Classes:
F16K11/04; F01C21/18; F03C2/00; F04C14/24; F15B11/06; F16K11/16; (IPC1-7): F04B49/02
Field of Search:
137/596,628,630.15 251
View Patent Images:
US Patent References:
3596679MANUALLY OPERABLE PILOT VALVE1971-08-03Sugden, Jr.
2380836Flow control apparatus1945-07-31Gottlieb

Foreign References:
Primary Examiner:
Wayner, William E.
Parent Case Data:


This is a continuation-in-part of patent application Ser. No. 781,061 filed Dec. 4, 1968, now abandoned, by the same inventor for a "Vane Type Motor Having Fluid Pressure Biased Valves."
What is claimed is

1. An improved valve assembly for sequentially providing a supply of pressurized fluid from a fluid inlet to first and second fluid outlets, comprising, in combination:

2. The improved valve assembly of claim 1 wherein said valve member is movable within said housing along an axis of translation and wherein said inlets and outlets are spaced from one another along said axis of translation.

3. The improved valve assembly of claim 1 wherein said valve member includes a land in sealing engagement with said housing and interposed between said outlets, said valve member being movable to said second position to provide said path from said inlet to both of said outlets.

4. The improved valve assembly of claim 1 wherein said means for sealing said exhaust opening is movable in said valve housing to connect said second outlet with said exhaust opening when said inlet is sealed.

5. The improved valve assembly of claim 1 wherein said valve member is movable along an axis of translation and including a second valve member translatable within said housing along the same axis of translation and in the opposite sense.

6. The improved valve assembly of claim 1 including a second separate valve member in said valve housing cooperative with a second inlet and another separate outlet in said housing, and means for moving one or the other of said valve members out of sealing engagement with its associated inlet.

7. The improved valve assembly of claim 1 including a second separate valve member in said valve housing cooperative with a second inlet and another separate outlet, two separate exhaust openings in said housing connectable respectively with an outlet of each valve member, and means for moving one or the other of said valve members out of sealing engagement with its associated inlet, said means for sealing movable to seal the exhaust opening associated with the valve member that is positioned to open its associated inlet.

8. The improved valve assembly of claim 7 wherein said means for moving said valve members and said means for sealing said exhaust openings comprise a plunger in said housing, intermediate said valve members and reciprocal to engage one or the other of said valve members.

9. The improved valve assembly of claim 1 wherein said means for sealing comprise a plunger slidable within said bore and having a radius substantially equal to the internal radius of said bore, said plunger also including a portion extending from one end thereof for guiding and engaging with said valve member.

10. The improved valve member of claim 1 wherein said valve member includes a surface area on the one side of said inlet which is greater than the surface area on the other side of said inlet so as to bias the valve member into a closed position by means of fluid pressure.

11. An improved valve assembly for sequentially providing a supply of pressurized fluid from a fluid inlet to first and second fluid outlets comprising, in combination:

12. The valve assembly of claim 11 wherein said valve housing is substantially cylindrical and wherein said first valve member comprises a spool within said housing and translatable along the longitudinal axis of said housing, said inlet comprising an open end of said housing, and wherein said first and second outlets comprise adjacent, spaced openings along the longitudinal axis of said housing.

13. The valve assembly of claim 12 wherein said spool includes an end seal for said inlet of said housing and wherein said spool also includes a landed surface bearing against the interior of said housing and providing a seal between said outlets.

14. The valve assembly of claim 11 wherein said exhaust opening in said housing is adjacent said second outlet and wherein said plunger is slidable in said housing to provide a fluid flow path between one of said outlets and said exhaust opening whenever said valve member is seated to close said inlet.


A common practice in vane type motors is to provide springs in the bottoms of the vane slots of the rotor which exert outward pressure on the vanes. Such springs are subject to fatigue, wear and eventual breakage. Sometimes gravity or centrifugal force are depended upon to bias the vanes outwardly in their slots. These forces are not always of the proper value for most efficient motor operation. Consequently, arrangements are often provided whereby the driving, pressurized fluid is diverted, in part, against the back side of the vanes. The vanes are biased outward by the continuous fluid pressure.

Fluid biased vanes are very desirable and can be controlled for efficient motor operation. However, when starting the motor the vanes ought to be biased outward prior to providing driving fluid for the motor. Such a preliminary outward biasing force is especially desirable for applications where the motor is constantly being turned on and off.


A passageway and port system are provided supplying fluid pressure to the bottoms of the slots in a rotor in which vanes are mounted that contact the inner surface of a stator surrounding the rotor. A control valve is provided which upon initial movement toward open position admits fluid pressure to the passageway and port system just mentioned to insure proper outward biasing of the vanes prior to motor operation. Thereafter the control valve may be used to meter the flow of fluid pressure to the motor. The motor and control valve are of reversing type so that my biasing system (also designed as a reversible one) is operable in either direction of rotation of the motor.

An object of the present invention is to provide an improved valve assembly having one inlet and at least two outlets.

A further object is to provide the valve bushing with admission seats for the poppet heads and metering flanges for the valve bore, the passageways leading to the vane slot ports being under initial control of the poppet heads and the inlet and exhaust ports being under secondary control of the valve actuating plunger and the metering flanges of the valve plugs, the control valve being thus a double-end type making possible its use in conjunction with a reversing type motor.

These and other objects, advantages and features of the invention will be set forth in the detailed description which follows.


In the detailed description which follows, reference will be made to the drawing comprised of the following figures:

FIG. 1 is a side elevation of a fluid pressure operated hoist as an example where my vane-type motor having fluid pressure biased vanes may be used, one portion of the hoist being shown in section which includes the motor and control valve;

FIG. 2 is a semi-diagrammatic exploded isometric view of the pg,4 parts of the motor and the control valve to show the relationship of such parts, the valve body and portions of the valve being shown in section at right angles to the valve shown in FIG. 1 to illustrate details;

FIG. 3 is a cross-sectional view of the valve assembly taken substantially along line 3--3 in FIG. 1;

FIG. 4 is a cross-sectional view of the interconnection between the first outlet of the valve assembly and the back side of the vanes;

FIGS. 5, 6 and 7 illustrate in partial schematic, cross-sectional views a symmetrical embodiment of the valve assembly of the invention in distinct operational position; and

FIGS. 8, 9 and 10 illustrate in partial schematic cross-sectional views an asymmetrical embodiment of the valve assembly of the invention in distinct operational positions.


On the accompanying drawing I have used the reference numeral 10 to indicate a hoist housing which houses a vane type motor of the kind herein contemplated and provided with fluid pressure biased vanes. A tubular stator 11 is located in the housing 10 and includes end plates 12 and 14 to form a complete closure for a rotor. FIG. 2 illustrates the stator 11 and the end plates 12 and 14 and also a rotor 15 which rotates inside the stator and which has substantially radial slots 18 in which vanes 16 slide with their outer ends in contact with the inner surface of the stator 11. The vanes 16 are contoured with beveled corners 17 to facilitate entry of fluid pressure under the inner ends of the vanes. The stator 11 is provided with inlet ports 20, secondary exhaust ports 22 and primary exhaust ports 24 for actuation of the motor as will hereinafter appear.

The motor shaft is shown at 26, FIG. 1, the rotor 15 being secured thereto as by a key 25. The left end of the motor shaft 26 extends into the left end of the housing 10 wherein suitable step-down gearing is provided for driving a bearing supported sleeve 27 at slow speed compared to the relatively high speed of the motor shaft 26. Since such gearing forms no part of my present invention, it is not shown on the drawings.

A chain wheel 28 is secured to the sleeve 27 and a hoisting chain 30 is trained thereover and terminates in a hoisting hook 32 to engage with a load to be hoisted, the housing 10 being suitably supported as by a supporting hook 34. A pendant control 36 is shown for controlling the fluid pressure operated motor comprising the stator 11, the rotor 15 and the vanes 16 as will hereinafter appear.

A control valve 37 which comprises the invention is shown in each FIGURE of the drawing and is of special construction with passageways for the inlet ports 20, the exhaust ports 22 and the bottoms of the vane slots 18 as shown diagrammatically in FIG. 2. The control valve 37 comprises a valve body 38 having a forward end F and a reverse end R. Slidable therein is a valve actuating piston or plunger 40, the valve body 38 being provided with a bore 42, having ends which serve metering purposes as will be explained. The plunger 40 has reduced ends or shafts 44 and 46 which are slidable relative to valve members or plugs 48F (forward) and 48R (reverse).

Referring particularly to FIGS. 2, 5, 6 and 7, the valve bushing 38 beyond the ends of the bore 42 is provided with chambers 50 (upper end in FIG. 2) and 52 (bottom end) terminating at the ends of the valve body in admission seats 54 and 56. Each valve plug 48F and 48R is provided with a poppet head 58F and 58R having O-rings normally seated against their adjacent admission seats 54 and 56 and a flange 60 normally in abutment with the adjacent outer end surface 61 of the metering bore 42.

A fluid pressure supply passageway 62 is shown diagrammatically in the FIGURES for supplying fluid pressure such as compressed air against the outer ends of the poppet heads 58F and 58R of the valve plugs 48F and 48R. An inlet passageway 70 leads from the upper end of the metering bore 42 (diagrammatically in FIG. 2) and through the end plate 14 whereupon it is continued as shown at 70 in the wall of the stator 11 to communicate with the inlet ports 20 of the stator. Similarly, an exhaust passageway 72 extends from the metering bore 42 adjacent to its lower end through the end plate 14 and into the stator 11 where it communicates with the secondary exhaust ports 22.

The end plate 14 is also provided with arcuate vane slot ports 64 and 66 as shown in FIG. 2 and these communicate by means of passageways 65 and 67 respectively with the chambers 50 and 52 of the valve bushing 38 as also shown diagrammatically in FIG. 2. FIG. 2 also shows an exhaust passageway system 68 diagrammatically which eventually opens to atmosphere through a suitable silencer in the usual way (not illustrated).

The control valve 37 is normally in neutral position when fluid pressure is supplied to the passageways 62 and thus to the outer ends of the poppet heads 58 so that the pressure tends to keep the poppet heads seated. The pendant control 36 is operable to rock a control shaft 74 having a pinion sector 76 secured to the right hand end thereof as shown in FIG. 1 and meshing with rack teeth 78 of the valve actuating plunger 40. The pendant control 36 usually comprises an "UP" handle and a "DOWN" handle whereby rocking the shaft 74 from the neutral position will move the plunger 40 and one or the other of the control valve plugs 48 of the valve 37 in one direction and will cause the motor to rotate in a forward direction or vice versa.

Reference is now made to FIGS. 5, 6 and 7 and, in particular, to the right hand or forward portion, F, of the valve assembly depicted therein. The plug 48F is slidably mounted on the shaft 44. Plug 48F includes a poppet head 58F with an outer valve portion 78 for engaging with seat 54. Flange or bushing 60 is also provided and seals the fluid flow passage between chamber 50 and a chamber 80 defined by the bushing 60 and plunger 40. As plunger 40 and thus shaft 44 and plug 48F translate or move to the right, fluid can flow in through inlet 62 and out through a first outlet 82. However, flange 60 remains in sealing contact with surface 61 as shown in FIG. 6. Thus, no fluid can flow through to a second outlet 84.

Further translation of plunger 40 causes flange 60 to open the passage to outlet 84 as shown in FIG. 7. Thus, fluid flow passes from inlet 62 through to the two outlets 82 and 84. In the embodiment shown, outlet 82 is connected with passage 65 so that upon initial translation of plunger 40, Fluid pressure is supplied to the base or bottom of vanes 16. Subsequently and sequentially upon further translation of plunger 40, the flow of fluid through outlet 84 fluid in this case, through passage 70. This activates or drives the rotary motor.

The width of flange 60 may be varied to control the dwell time, i.e. the time during which fluid flows from inlet 62 to only outlet 82 as the plunger 40 is being translated at a uniform speed in body 38. The outlet 84 may also be maintained in a closed position by translating the plunger for a limited distance as illustrated in FIG. 6. In any event, fluid flows sequentially first through outlet 82 and then through both outlets 82 and 84.

In FIGS. 5, 6 and 7, the valve assembly is symmetrical in construction. Thus, the plug 48R on shaft 46 is constructed in the same manner as the plug 48F previously described on shaft 44. Operation is also the same except that it occurs when the plunger 40 is translated to the left.

As a further feature, an exhaust outlet or passage 86F is also associated with each plug 48. Thus, as plunger 40 is translated to the left in FIGS. 5, 6 and 7, the head 58 seats on seat 54 and ultimately plunger 40 moves to permit fluid flow between outlets 84 and 86. In practical application as applied to the hoist described above, fluid may exhaust from outlet 86F through outlet 84F as also shown in FIG. 2. In a similar manner when plunger 40 translates to the right, fluid may exhaust through the outlet 86R.

Note that the symmetrical valve assembly of FIGS. 5, 6 and 7 provides for exhaust of one side of the assembly while simultaneously providing for fluid supply via the opposite side of the assembly. Also, a separate plug 48 is associated with each side of the valve assembly whereas a single plunger 40 is associated therewith. In operation, the valve assembly as incorporated in an air hoist of the type described positively drives the vanes outward in their slots prior to causing the rotary motor to operate.

Other uses of the valve assembly are also possible, particularly where a first fluid flow is required before a second fluid flow. In addition, the symmetrical assembly of FIGS. 5, 6 and 7 permits reversible operation of apparatus by means of the valve assembly of the invention. Such reversing operation has utility for applications other than with reversible rotary air motors.

Reference is now made to FIGS 3, 8, 9 and 10, wherein there is illustrated an asymmetrical valve assembly. The forward plug 48F is identical in construction to that previously described. Likewise, operation of the forward plug and its associated flange 60 is the same. However, an asymmetrical plug 88 is provided for cooperation with shaft 46. The flange 60 has been eliminated from plug 88. Of course, the elimination of the flange 60 also eliminates the sequencing arrangement possible with the plug 48. Therefore, the valve assembly of FIGS. 3, 8, 9 and 10 operates through plug 48F to provide sequential fluid flow and exhaust through exhaust outlet 86 and second outlet 84. Plug 88 merely permits fluid flow from inlet 62 to an outlet 84R or from exhaust outlet 86R through outlet 84R.

The construction of FIGS. 3, 8, 9 and 10 was found quite acceptable for utilization in a rotary motor hoist since sequential operation of the motor is not deemed essential when the motor is reversed in order to lower chain 30.