US3225786A - Vane pressurizing means - Google Patents

Vane pressurizing means Download PDF

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US3225786A
US3225786A US238602A US23860262A US3225786A US 3225786 A US3225786 A US 3225786A US 238602 A US238602 A US 238602A US 23860262 A US23860262 A US 23860262A US 3225786 A US3225786 A US 3225786A
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passages
port
radially spaced
motor
housing structure
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US238602A
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John L Elliott
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Tracer Control Co
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Tracer Control Co
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K27/00—Construction of housing; Use of materials therefor
    • F16K27/02—Construction of housing; Use of materials therefor of lift valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7771—Bi-directional flow valves
    • Y10T137/7779—Axes of ports parallel
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7837—Direct response valves [i.e., check valve type]
    • Y10T137/7838—Plural

Definitions

  • This invention relates to hydraulic motors and more particularly to a means for pressurizing the vanes of such motors.
  • a further object of the invention is to facilitate pressurizing of the vanes of a vane-type hydraulic motor by providing a simplified pressure delivery system selfcontained as a readily manufactured manifold and valve unit.
  • FIG. 1 is a diagrammatic representation of the vane pressurizing means of the present invention.
  • FIG. 2 is a view of a preferred embodiment of the present invention showing the manifold and valve members in longitudinal cross section taken substantially at line 2-2 of FIG. 3.
  • FIG. 3 is a plan view of the valve member and plate member 49 of the present invention as seen on line 3-3 of FIG. 2.
  • FIG. 4 is a cross sectional view taken substantially on line 44 of FIG. 3, and
  • FIG. 5 is a plan view of the manifold member of the present invention as seen on line 55 of FIG. 2.
  • FIG. 1 a hydraulic motor is shown diagrammatically in FIG. 1 as comprising a housing 11 having a chamber 12 defined by a cam ring 13 and a rotor 14.
  • the rotor 14 is provided with a plurality of radial slots 15 although for convenience only one is shown in FIG. 1.
  • Each of the slots 15 carries a radially slidable vane member 16.
  • a passage 17 communicates with the slots 15.
  • a manifold member 18 is preferably adapted to be carried intermediate a valve member 19 and a four way control valve 20.
  • the valve member 19 is carried by the motor 10.
  • the manifold member 18 preferably comprises a housing structure 21 having a pressure inlet 22 adapted for connection to a source of fluid pressure and an exhaust port 23.
  • the pressure inlet 22 communicates with a pressure passage 22a which in turn is connected to a passage 24 provided in the control valve 20 and the control valve 20 is provided with an exhaust passage 25 communicating with an exhaust passage 23a provided in the manifold member 18 and which registers with the exhaust port 23.
  • the housing structure 21 is further provided with a pair of spaced ports 26-27 communicating with ports 28-29 respectively, provided in the control valve 20. Angularly disposed passages 34-35 provided in the housing structure 21 communicate with the ports 26-27 respectively.
  • valve member 19 preferably comprises a housing structure 39 having a central chamber 40 and radially spaced parallel passages 41-42-43 and similarly spaced passages 44-45-46.
  • Plate members 47, 48 and 49 are carried intermediate the housing structure 39 and the manifold member 18 and similar plate members 52-53-54 are carried intermediate the housing structure 39 and the motor 10.
  • the plate member 47 is provided with perforations 55 and 56 registering with the angular passages 34 and 35 respectively of the manifold member 18.
  • the plate member 48 is provided with perforations 5758 axially aligned with and of a smaller diameter than the perforations 55-56 respectively.
  • Perforations 60-61 in the plate member 49 provide communication between the perforations 5758 and the passages 41-42-43 and 44-45-46 respectively.
  • O-ring seals 62 are carried in the perforations 55, 56, 60 and 61 to prevent fluid leakage between the manifold member 18, the plate members 47, 48 and 49 and valve member 19.
  • the plate member 54 is provided with perforations 64-65 which are positioned to register with ports 67-68 respectively, provided in the motor 10 and which open to the chamber 12. Perforations 69-70 of a smaller diameter are provided in the plate member 53 in axial alignment with the perforations 64-65 respectively.
  • the plate member 52 is provided with perforations 71-72 communicating with the passages 41-42-43 and 44-45-46 respectively. O-ring seals 73 are provided in the perforations 64, 65, 71 and 72 to prevent fluid leakage between the valve member 19, the plate members 52, 53 and 54, and the motor 10.
  • a check valve 74 is carried in the passage 41 and is operable to open fluid flow from the passage 34 to the port 67 upon sensing a predetermined pressure in passage 41.
  • the plate member 53 provides the seat for a spring 75 urging the check valve 74 to a normally closed position.
  • a check valve 76 is carried in the passage 42 and is operable to open fluid flow from the port 67 to the passage 34 upon sensing a predetermined pressure in passage 42.
  • a spring 77 seated against the plate member 48 urges the check valve 76 toward a normally closed position.
  • a check valve 80 is carried in the passage 45 and is operable to open fluid flow from the passage 35 to the port 68 upon sensing a predetermined pressure in the passage 45.
  • a spring 81 seated against the plate member 53 urges the check valve 80 toward a normally closed position.
  • a check valve 82 is carried in the passage 44 and is operable upon sensing a predetermined pressure in the passage 44 to open fluid flow from the port 68 to the passage 35.
  • the plate member 48 provides the seat for a spring 83 which urges the check valve 82 toward a normally closed position.
  • angular passages 85-86 provide communication between the chamber 41 and the passages 43 and 46 respectively. Seals 87-88 are provided in the passages 43 and 46 respectively to prevent fluid flow from the passages 43-46 to the ports 67-68 respectively.
  • a check valve 89 is carried in the passage 43 and is operable to open fluid flow from the passage 34 to the chamber 40 upon sensing a predetermined pressure in the passage 43.
  • a spring 90 urges the check valve 89 toward a normally closed position.
  • a check valve 92 is carried in the passage 46 and is operable to open fluid flow from the passage 35 to the chamber 40 upon sensing a predetermined pressure in passage 46.
  • a spring 93 urges the check valve 92 toward a normally closed posi tion.
  • the chamber 40 is connected to the passage 17 in the motor by conduit 94.
  • the motor 10 is preferably of the type presently being manufactured by Vickers Incorporated and described by that company as the M2-200S2 series. Rotation of this type of a motor is either clockwise or counter-clockwise depending upon whether pressure is directed to the port 67 or the port 68.
  • the control valve 20 is selectively operable to direct fluid under pressure to either of the passages 34-35 and to exhaust through the other.
  • a control valve 20 which has been found to be satisfactory in the preferred embodiment of the present invention is a Model l40-D Electro-Hydraulic Servo-Valve presently being manufactured by Pegasus Laboratories Inc., of Berkley, Michigan.
  • check valves 74 and 80 In operation it has been preferred to construct the check valves 74 and 80 to respond to a pressure value of 65 p.s.i. and the check valves 82, 92, 76 and 89 to respond to a pressure of 5 p.s.i. although it will be apparent that other values can be selected to open these valves without departing from the spirit of the invention.
  • the pressure inlet 22 of the manifold member 18 is adapted for connection to a source of fluid pressure and directs fluid under pressure to the control valve 20.
  • all check valves 74, 76, 80, 82, 89 and 92 are closed and the vane members 16 are static in the slots 15.
  • Positioning the control valve 20 to direct slight flow to the passage 26 of the manifold member 18 and to permit exhaust through the passages 27-29, the exhaust passage 25, and the exhaust port 23 will have the following effect:
  • check valve 74 opens and fiow takes place through port 67 to chamber 12 resulting in tangential pressure on vane 16 in a counter-clockwise direction and rotation of rotor 14 in the same direction. Oil ahead of the vane 16 is forced through check valve 82, passages 35, 27, 29 and exhausts through 23.
  • radial vane pressure will be approximately 65 p.s.i. above tangential vane pressure when flow occurs through check valve 74, because of the resultant pressure drop across check valve 74.
  • the check valves 80, 92 and 76 operate substantially as described above when pressure is directed to the passage 27 by the control valve 20 to produce clockwise rotation of the motor 10.
  • manifold member 18 andthe valve member 19 of the present invention can be readily manufactured and assembled.
  • the plate members 47-49 and 52-54 can be readily and inexpensively produced.
  • the housings 21 and 39 can be drilled and the check valves positioned.
  • the plate members 48 and 53 provide the seats for the check valves and the whole assembly then can be bolted together.
  • a combination manifold and valve assembly adapted for use with a sliding vane type reversible hydraulic motor having a first and a second port for alternately receiving and discharging a working fluid depending upon the direction of operation of the motor and a third port for receiving a fiuid to urge the vanes of the motor outwardly, said manifold and vane assembly comprising,
  • a check valve being positioned in each of said radially spaced passages and means providing communication between one of said first housing structure passages and said first plurality of radially spaced passages and means providing communication be tween the other of said first housing structure passages and said second plurality of radially spaced passages,
  • (h) means blocking fluid from said third port means connected passages to said first and second port means.
  • said check valves each includes a spring member
  • said communication providing means includes a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations and being of smaller diameter than said first plate member perforations to provide portions extending across said first plate member perforations
  • said check valves each includes a spring member
  • said first and second port means includes a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations aligned respectively with said first plate member perforations and being of a smaller diameter than said first plate member perforations to provide portions extending across said first plate member perforations,
  • a combination manifold and valve assembly comprising,
  • said housing structure further being provided with a first port means, a second port means, and a third port means,
  • a check valve being disposed in each of said radially spaced passages with at least two of said check valves in each of said first and second plurality of passages being disposed in opposite directions whereby fluid may be alternately directed to and from said first and second port means depending upon the position of said valve means, and
  • check valves being disposed in those passages of said first plurality of passages and said second plurality of passages which are connected to said third port means being normally closed and being operable to open flow to said third port means at a predetermined pressure whereby fluid flow through said third port means is opened upon a predetermined pressure being provided by said valve means at either of said first or second passages.
  • each of said check valves includes a spring internmer
  • said housing structure comprises a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations aligned respectively with said first plate member perforations and being of a smaller diameter than said first plate member perforations to provide portions extending across said first plate member perforations, and
  • each of said check valves includes a spring member
  • said first and second port means includes a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations aligned respectively with said first plate member perforations and being of a smaller diameter than said first plate member perforations whereby to provide portions extending across said first plate member perforations,
  • a combination manifold and valve assembly comprising (a) a first housing structure having a pair of spaced passages and valve means selectively operable to deliver fluid under pressure to either of said passages,
  • a check valve being positioned in each of said radially spaced passages and means providing communication between one of said first housing structure passages and said first plurality of radially spaced passages and means providing communication between the other of said first housing structure passages and said second plurality of radially spaced passages,
  • check valves being carried in said third port means connected radially spaced passages being normally closed and being operableto open in a direction toward said third portmeans whereby upon a predetermined pressure being produced in either of said first and second passages of said first housing structure fluid under pressure is directed to said third port means.

Description

Dec. 28, 1965 J. ELLIOTT 3,225,786
VANE PRESSURIZING MEANS Filed Nov. 19, 1962 2 Sheets-Sheet 1 INVENTOR.
(John L. E///'Of7 ATTORNEYS Dec. 28, 1965 J. L. ELLIOTT 3,225,785
VANE PRESSURIZING MEANS Filed Nov. 19, 1962 2 Sheets-Sheet 2 INVENTOR.
F15. 5. afli A T701 NE 75 United States Patent 3,225,786 VANE PRESSURIZING MEANS John L. Elliott, Birmingham, Mich., assignor to Tracer Control Company, Hazel Park, Mich., a corporation of Michigan Filed Nov. 19, 1962, Ser. No. 238,602 11 Claims. (Cl. 137-512) This invention relates to hydraulic motors and more particularly to a means for pressurizing the vanes of such motors.
Present vane pressurizing of vane type hydraulic motors is generally accomplished by bringing a line directly from the pressure supply source to the inner ends of vanes. In this way the constant high pressure of the supply is directed to the underside of the vanes regardless of the pressure being utilized to operate the motor. This pressure forces the vanes radially outwardly against the inside face of the cam ring at a constant high pressure. However, rotation of the motor does not begin until the tangential force on the vanes overcomes the static friction force of the vanes being held against the inner surface of the cam ring. When suflicient pressure is developed to rotate the motor a breakway action occurs. This immediately reduces the pressure necessary to continue rotation of the motor. The radial force on the vanes that causes them to act as radial friction brakes causing the motor to slow down. The entire process then repeats itself causing jerky, intermittent rotation of the motor. Such operation is especially undesirable when low speed, low torque and immediate response are required of the system.
It is then an object of the present invention to increase the efficiency of vane type hydraulic motors by providing a combination manifold and valve assembly for such motors having means of maintaining a constant radial and tangential pressure differential across the vanes during operation of the motor regardless of the operating pressure necessary for rotation of the motor at various speeds.
A further object of the invention is to facilitate pressurizing of the vanes of a vane-type hydraulic motor by providing a simplified pressure delivery system selfcontained as a readily manufactured manifold and valve unit.
Still further objects and advantages will readily occur to one skilled in the art to which the invention pertains upon reference to the accompanying drawings in which like reference characters refer to like parts throughout the several views and in which FIG. 1 is a diagrammatic representation of the vane pressurizing means of the present invention.
FIG. 2 is a view of a preferred embodiment of the present invention showing the manifold and valve members in longitudinal cross section taken substantially at line 2-2 of FIG. 3.
FIG. 3 is a plan view of the valve member and plate member 49 of the present invention as seen on line 3-3 of FIG. 2.
FIG. 4 is a cross sectional view taken substantially on line 44 of FIG. 3, and
FIG. 5 is a plan view of the manifold member of the present invention as seen on line 55 of FIG. 2.
Now referring to the drawings for a more detailed description of the present invention a hydraulic motor is shown diagrammatically in FIG. 1 as comprising a housing 11 having a chamber 12 defined by a cam ring 13 and a rotor 14. The rotor 14 is provided with a plurality of radial slots 15 although for convenience only one is shown in FIG. 1. Each of the slots 15 carries a radially slidable vane member 16. A passage 17 communicates with the slots 15.
Patented Dec. 28, 1965 As can best be seen in FIGS. 1 and 2 a manifold member 18 is preferably adapted to be carried intermediate a valve member 19 and a four way control valve 20. The valve member 19 is carried by the motor 10.
As can best be seen in FIGS. 1, 2 and 5, the manifold member 18 preferably comprises a housing structure 21 having a pressure inlet 22 adapted for connection to a source of fluid pressure and an exhaust port 23. The pressure inlet 22 communicates with a pressure passage 22a which in turn is connected to a passage 24 provided in the control valve 20 and the control valve 20 is provided with an exhaust passage 25 communicating with an exhaust passage 23a provided in the manifold member 18 and which registers with the exhaust port 23. The housing structure 21 is further provided with a pair of spaced ports 26-27 communicating with ports 28-29 respectively, provided in the control valve 20. Angularly disposed passages 34-35 provided in the housing structure 21 communicate with the ports 26-27 respectively.
As can best be seen in FIGS. 2, 3 and 4 the valve member 19 preferably comprises a housing structure 39 having a central chamber 40 and radially spaced parallel passages 41-42-43 and similarly spaced passages 44-45-46.
Plate members 47, 48 and 49 are carried intermediate the housing structure 39 and the manifold member 18 and similar plate members 52-53-54 are carried intermediate the housing structure 39 and the motor 10. The plate member 47 is provided with perforations 55 and 56 registering with the angular passages 34 and 35 respectively of the manifold member 18. The plate member 48 is provided with perforations 5758 axially aligned with and of a smaller diameter than the perforations 55-56 respectively. Perforations 60-61 in the plate member 49 provide communication between the perforations 5758 and the passages 41-42-43 and 44-45-46 respectively. O-ring seals 62 are carried in the perforations 55, 56, 60 and 61 to prevent fluid leakage between the manifold member 18, the plate members 47, 48 and 49 and valve member 19.
The plate member 54 is provided with perforations 64-65 which are positioned to register with ports 67-68 respectively, provided in the motor 10 and which open to the chamber 12. Perforations 69-70 of a smaller diameter are provided in the plate member 53 in axial alignment with the perforations 64-65 respectively. The plate member 52 is provided with perforations 71-72 communicating with the passages 41-42-43 and 44-45-46 respectively. O-ring seals 73 are provided in the perforations 64, 65, 71 and 72 to prevent fluid leakage between the valve member 19, the plate members 52, 53 and 54, and the motor 10.
As can best be seen in FIG. 2, a check valve 74 is carried in the passage 41 and is operable to open fluid flow from the passage 34 to the port 67 upon sensing a predetermined pressure in passage 41. The plate member 53 provides the seat for a spring 75 urging the check valve 74 to a normally closed position. A check valve 76 is carried in the passage 42 and is operable to open fluid flow from the port 67 to the passage 34 upon sensing a predetermined pressure in passage 42. A spring 77 seated against the plate member 48 urges the check valve 76 toward a normally closed position.
A check valve 80 is carried in the passage 45 and is operable to open fluid flow from the passage 35 to the port 68 upon sensing a predetermined pressure in the passage 45. A spring 81 seated against the plate member 53 urges the check valve 80 toward a normally closed position. A check valve 82 is carried in the passage 44 and is operable upon sensing a predetermined pressure in the passage 44 to open fluid flow from the port 68 to the passage 35. The plate member 48 provides the seat for a spring 83 which urges the check valve 82 toward a normally closed position.
As can best be seen in FIGS. 3 and 4 angular passages 85-86 provide communication between the chamber 41 and the passages 43 and 46 respectively. Seals 87-88 are provided in the passages 43 and 46 respectively to prevent fluid flow from the passages 43-46 to the ports 67-68 respectively. A check valve 89 is carried in the passage 43 and is operable to open fluid flow from the passage 34 to the chamber 40 upon sensing a predetermined pressure in the passage 43. A spring 90 urges the check valve 89 toward a normally closed position. A check valve 92 is carried in the passage 46 and is operable to open fluid flow from the passage 35 to the chamber 40 upon sensing a predetermined pressure in passage 46. A spring 93 urges the check valve 92 toward a normally closed posi tion. The chamber 40 is connected to the passage 17 in the motor by conduit 94.
The motor 10 is preferably of the type presently being manufactured by Vickers Incorporated and described by that company as the M2-200S2 series. Rotation of this type of a motor is either clockwise or counter-clockwise depending upon whether pressure is directed to the port 67 or the port 68.
The control valve 20 is selectively operable to direct fluid under pressure to either of the passages 34-35 and to exhaust through the other. A control valve 20 which has been found to be satisfactory in the preferred embodiment of the present invention is a Model l40-D Electro-Hydraulic Servo-Valve presently being manufactured by Pegasus Laboratories Inc., of Berkley, Michigan.
In operation it has been preferred to construct the check valves 74 and 80 to respond to a pressure value of 65 p.s.i. and the check valves 82, 92, 76 and 89 to respond to a pressure of 5 p.s.i. although it will be apparent that other values can be selected to open these valves without departing from the spirit of the invention.
The pressure inlet 22 of the manifold member 18 is adapted for connection to a source of fluid pressure and directs fluid under pressure to the control valve 20. With the control valve 20 in a closed position, all check valves 74, 76, 80, 82, 89 and 92 are closed and the vane members 16 are static in the slots 15. Positioning the control valve 20 to direct slight flow to the passage 26 of the manifold member 18 and to permit exhaust through the passages 27-29, the exhaust passage 25, and the exhaust port 23 will have the following effect:
Pressure builds up in passages 26, 34, 41 and 43. When this pressure reaches 5 p.s.i., check valve 89 opens allowing flow through passage 85, chamber 40, conduit 94, passage 17 to slots 15. Pressure will then build under vanes 16 which will slide radially outward until stopped by the inner surface of cam ring 13. Pressure now continues to rise in passages 26, 34, 41 and 43. Slight flow takes place through check valve 89 and through slots around sides and ends of vanes 16 into chamber 12, through port 68 and into passage 44. When pressure in passage 44 reaches 5 p.s.i., check valve 82 opens and flow takes place through passages 35, 27 and 29 and exhausts through 23. This slight flow may continue and the rotor 14 will remain stationary until pressure in passage 34 builds up to 65 p.s.i. At this point, check valve 74 opens and fiow takes place through port 67 to chamber 12 resulting in tangential pressure on vane 16 in a counter-clockwise direction and rotation of rotor 14 in the same direction. Oil ahead of the vane 16 is forced through check valve 82, passages 35, 27, 29 and exhausts through 23.
Positioning the control valve to permit more flow in the same direction will result in higher r.p.m. of rotor 14. Regardless of rotor 14, rpm. or load, radial vane pressure will be approximately 65 p.s.i. above tangential vane pressure when flow occurs through check valve 74, because of the resultant pressure drop across check valve 74.
After the vanes once contact cam ring 13, flow will be slight through check valve 89 producing only a slight pressure drop across check valve 89.
The check valves 80, 92 and 76 operate substantially as described above when pressure is directed to the passage 27 by the control valve 20 to produce clockwise rotation of the motor 10.
By this method the radial and tangential vane pressure differential remains constant as long as there is flow through the motor 10 no matter what operating pressure is necessary to produce rotation. This eliminates intermittent and jerky operation of the motor 10. Although 65 p.s.i. has been preferred as the constant pressure differential in the embodiment described, it is apparent that this value can be readily changed by changing the value at which the check valves will respond.
It is also apparent that the manifold member 18 andthe valve member 19 of the present invention can be readily manufactured and assembled. The plate members 47-49 and 52-54 can be readily and inexpensively produced. The housings 21 and 39 can be drilled and the check valves positioned. The plate members 48 and 53 provide the seats for the check valves and the whole assembly then can be bolted together.
Although I have described but one embodiment of the present invention, other changes and modifications may be made without departing from the spirit of the invention or the scope of the appended claims.
I claim:
1. A combination manifold and valve assembly adapted for use with a sliding vane type reversible hydraulic motor having a first and a second port for alternately receiving and discharging a working fluid depending upon the direction of operation of the motor and a third port for receiving a fiuid to urge the vanes of the motor outwardly, said manifold and vane assembly comprising,
(a) a first housing structure having a pair of spaced passages and valve means selectively operable to deliver fluid under pressure to either of said passages,
(b) a second housing structure having a first plurality of radially spaced through passages and a second plurality of radially spaced through passages,
(c) a check valve being positioned in each of said radially spaced passages and means providing communication between one of said first housing structure passages and said first plurality of radially spaced passages and means providing communication be tween the other of said first housing structure passages and said second plurality of radially spaced passages,
(d) a first port means adapted for connection to the first port of said motor and registering with said first plurality of radially spaced passages and a second port means adapted for connection with said second port of said motor and registering with said second plurality of radially spaced passages,
(e) at least two of said check valves in each of said first and second plurality of radially spaced passages being disposed in opposite directions whereby fluid may be alternately directed to and from said first and second port means depending upon the position of said valve means,
(f) a third port means provided in said second housing structure adapted for connection to said third port of said motor and a first passage connecting one of said first plurality of radially spaced passages to said third port means and a second passage provided in said second housing connecting one of said second plurality of radially spaced passages to said third port means,
(g) said check valves being carried in said third port means connected radially spaced passages being operable to open in the same direction, and
(h) means blocking fluid from said third port means connected passages to said first and second port means.
S 2. The combination as defined in claim 1 and in which, (a) said check valves each includes a spring member, (b) said communication providing means includes a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations and being of smaller diameter than said first plate member perforations to provide portions extending across said first plate member perforations,
(c) said spring member of at least one of said check valves being seated against said second plate member portion.
3. The combination as defined in claim 1 and in which,
(a) said check valves each includes a spring member,
(b) said first and second port means includes a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations aligned respectively with said first plate member perforations and being of a smaller diameter than said first plate member perforations to provide portions extending across said first plate member perforations,
(c) said spring member of at least one of said check valves being seated against said second plate member portion.
4. The combination as defined in claim 1 and in which said check valves being carried in said third port means connected radially spaced passages are operable to open at a different fluid pressure than at least one of said other check valves carried in each of said first and second plurality of radially spaced passages.
5. The combination as defined in claim 1 and in which said check valves being carried in said third port means connected radially spaced passages are operable to open at a lower fluid pressure than at least one of said other check valves carried in each of said first and second plu rality of radially spaced passages.
6. A combination manifold and valve assembly comprising,
(a) a housing structure having a first passage and a second passage and valve means selectively operable to deliver fluid under pressure to either of said passages,
(b) said housing structure further being provided with a first port means, a second port means, and a third port means,
(c) a first plurality of radially spaced passages being provided in said housing structure connecting said first passage with said first port means and a second plurality of radially spaced passages being provided in said housing structure connecting said second passage with said second port means,
(d) means connecting one of said first plurality of passages with said third port means and means connecting one of said second plurality of passages with said third port means,
(e) a check valve being disposed in each of said radially spaced passages with at least two of said check valves in each of said first and second plurality of passages being disposed in opposite directions whereby fluid may be alternately directed to and from said first and second port means depending upon the position of said valve means, and
(f) said check valves being disposed in those passages of said first plurality of passages and said second plurality of passages which are connected to said third port means being normally closed and being operable to open flow to said third port means at a predetermined pressure whereby fluid flow through said third port means is opened upon a predetermined pressure being provided by said valve means at either of said first or second passages.
7. The combination as defined in claim 6 and in which (a) each of said check valves includes a spring internmer,
(b) said housing structure comprises a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations aligned respectively with said first plate member perforations and being of a smaller diameter than said first plate member perforations to provide portions extending across said first plate member perforations, and
(c) said spring member of at least one of said check valves seated against said second plate member portion.
8. The combination as defined in claim 6 and in which (a) each of said check valves includes a spring member,
(b) said first and second port means includes a first plate member having a pair of perforations respectively registering with said first and second plurality of radially spaced passages, and a second plate member having perforations aligned respectively with said first plate member perforations and being of a smaller diameter than said first plate member perforations whereby to provide portions extending across said first plate member perforations,
(c) said spring member of at least one of said check valves being seated against said second plate member portion.
9. A combination manifold and valve assembly comprising (a) a first housing structure having a pair of spaced passages and valve means selectively operable to deliver fluid under pressure to either of said passages,
(b) a second housing structure having a pair of first plurality of radially spaced through passages and a second plurality of radially spaced through passages,
(c) a check valve being positioned in each of said radially spaced passages and means providing communication between one of said first housing structure passages and said first plurality of radially spaced passages and means providing communication between the other of said first housing structure passages and said second plurality of radially spaced passages,
(d) a first port means registering with said first plurality of radially spaced passages and a second port means registering with said second plurality of radially spaced passages,
(e) at least two of said check valves in each of said first and second plurality of radially spaced passages being disposed in opposite direct-ions whereby fluid may be alternately directed to and from said first and second port means depending upon the position of said valve means at a predetermined pressure,
(f) a third port means provided in said housing structure,
(g) a first passage provided in said second housing structure connecting said first plurality of radially spaced passages to said third port means and a second passage provided in said second housing structure connecting one of said second plurality of radially spaced passages to said third port means, and
(h) said check valves being carried in said third port means connected radially spaced passages being normally closed and being operableto open in a direction toward said third portmeans whereby upon a predetermined pressure being produced in either of said first and second passages of said first housing structure fluid under pressure is directed to said third port means.
10. The combination as defined in claim 9 and including means blocking fluid flow from each of said third port References Cited by the Examiner UNITED STATES PATENTS 2,255,784 9/1941 Kendrick 91138 10 M. CARY NELSON,
Kendrick.
Kendrick.
Kay 91-138 Tweedale 103-136 X Douglas 91138 Klessig et a1. 91-138 Oxley et al. 25l367 X Chuba 137-493.8 X
Carls 137625.69
Primary Examiner.
WILBUR I. GOODLIN, Examiner.

Claims (1)

1. A COMBINATION MANIFOLD AND VALVE ASSEMBLY ADAPTED FOR USE WITH A SLIDING VANE TUPE REVERSIVLE HYDRAULIC MOTOR HAVING A FIRST AND A SECOND PORT FOR ALTERNATELY RECEIVING AND DISCHARGING A WORKING FLUID DEPENDING UPON THE DIRECTION OF OPERATION OF THE MOTOR AND A THIRD PORT FOR RECEIVING A FLUID TO URGE THE VANES OF THE MOTOR OUTWARDLY, SAID MANIFOLD AND VANE ASSEMBLY COMPRISING, (A) A FIRST HOUSING STRUCTURE HAVING A PAIR OF SPACED PASSAGES AND VALVE MEANS SELECTIVELY OPERABLE TO DELIVER FLUID UNDER PRESSURE TO EITHER OF SAID PASSAGES, (B) A SECOND HOUSING STRUCTURE HAVING A FIRST PLURALITY OF RADIALLY SPACED THROUGH PASSAGES AND A SECOND PLURALITY OF RADIALLY SPACED THROUGH PASSAGES, (C) A CHECK VALVE BEING POSITIONED IN EACH OF SAID RADIALLY SPACED PASSAGES AND MEANS PROVIDING COMMUNICATION BETWEEN ONE OF SAID FIRST HOUSING STRUCTURE PASSAGES AND SAID FIRST PLURALITY OF RADIALLY SPACED PASSAGES AND MEANS PROVIDING COMMUNICATION BETWEEN THE OTHER OF SAID FIRST HOUSING STRUCTURE PASSAGES AND SAID SECOND PLURALITY OF RADIALLY SPACED PASSAGES, (D) A FIRST PORT MEANS ADAPTED FOR CONNECTION TO THE FIRST PORT OF SAID MOTOR AND REGISTERING WITH SAID FIRST PLURALITY OF RADIALLY SPACED PASSAGES AND A SECOND PORT OF SAID ADAPTED FOR CONNECTION WITH SAID SECOND PORT OF SAID MOTOR AND REGISTERING WITH SAID SECOND PLURALITY OF RADIALLY SPACED PASSAGES, (E) AT LEAST TWO OF SAID CHECK VALVES IN EACH OF SAID FIRST AND SECOND PLURALITY OF READIALLY SPACED PASSAGES BEING DISPOSED IN OPPOSITE DIRECTIONS WHEREBY FLUID MAY BE ALTERNATELY DIRECTED TO AND FROM SAID FIRST AND SECOND PORT MEANS DEPENDING UPON THE POSITION OF SAID VALVE MEANS, (F) A THIRD PORT MEANS PROVIDED IN SAID SECOND HOUSING STRUCTURE ADAPTED FOR CONNECTION TO SAID THIRD PORT OF SAID MOTOR AND A FIRST PASSAGE CONNECTING ONE OF SAID FIRST PLURALITY OF RADIALLY SPACED PASSAGES TO SAID THIRD PORT MEANS AND A SECOND PASSAGE PROVIDED IN SAID SECOND HOUSING CONNECTING ONE OF SAID SECOND PLURALITY OF RADIALLY SPACED PASSAGES TO SAID THIRD PORT MEANS, (G) SAID CHECK VALVES BEING CARRIED IN SAID THIRD PORT MEANS CONNECTED RADIALLY SPACED PASSAGES BEING OPERABLE TO OPEN IN THE SAME DIRECTION, AND (H) MEANS BLOCKING FLUIG FROM SAID THIRD PORT MEANS CONNECTED PASSAGES TO SAID FIRST AND SECOND PORT MEANS.
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Cited By (19)

* Cited by examiner, † Cited by third party
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US3381584A (en) * 1965-05-07 1968-05-07 Abegg & Reinhold Co Vane type rotary devices
US3450004A (en) * 1967-06-06 1969-06-17 Biasi Charles P De Auto-kinetic wheel or fluid motor
US3610272A (en) * 1968-07-05 1971-10-05 Blease Medical Equipment Ltd Valve block
US4052929A (en) * 1973-02-07 1977-10-11 Danfoss A/S Hydraulic control means, especially a steering means
US4301832A (en) * 1980-05-19 1981-11-24 Smith Dale R Pressure converter valve
US4331120A (en) * 1978-10-31 1982-05-25 Toyota Jidosha Kogyo Kabushiki Kaisha Device for controlling evaporative emission from an automobile
US20140216574A1 (en) * 2013-02-01 2014-08-07 Denso Corporation Relief valve
US20170031371A1 (en) * 2015-07-27 2017-02-02 Proserv Operations, Inc. Dynamic variable orifice
US10487951B2 (en) 2016-01-22 2019-11-26 Proserv Operations, Inc. Non-interflow directional control valve
US10584561B2 (en) 2014-01-03 2020-03-10 Proserv Operations, Inc. Dirty fluid pressure regulator and control valve
US10591076B2 (en) 2016-09-15 2020-03-17 Proserv Operations, Inc. Low friction hydraulic circuit control components
US10633951B2 (en) 2017-09-22 2020-04-28 Proserv Operations, Inc. Pressure regulator with user selectable dampening
US10670155B2 (en) 2015-10-05 2020-06-02 Proserv Gilmore Valve Llc Latching poppet valve
US10739796B2 (en) 2017-09-22 2020-08-11 Proserv Gilmore Valve Llc Pressure regulator with reconfigurable hydraulic dampening
US11022226B2 (en) 2018-03-20 2021-06-01 Proserv Operations, Inc. Microfluidic valve
US11054050B2 (en) 2018-08-13 2021-07-06 Proserv Operations Inc. Valve with press-fit insert
US11209096B2 (en) 2018-11-19 2021-12-28 Proserv Operations, Inc. Bilateral and throttling directional control valve
US11261982B2 (en) 2019-06-27 2022-03-01 Proserv Gilmore Valve Llc Pressure relief valve with bi-directional seat
US11828370B2 (en) 2020-01-02 2023-11-28 Proserv Gilmore Valve Llc Check valve with conforming seat

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US2826176A (en) * 1955-07-26 1958-03-11 United Shoe Machinery Corp Fluid motors for fastener inserting devices
US2947320A (en) * 1954-11-08 1960-08-02 Robotyper Corp Convertible valve structure
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US2453309A (en) * 1939-12-29 1948-11-09 Oilgear Co Vane type hydraulic motor
US2255784A (en) * 1940-05-24 1941-09-16 Manly Corp Fluid pressure device
US2255786A (en) * 1940-09-14 1941-09-16 Manly Corp Reversible vane type fluid motor
US2319238A (en) * 1941-09-12 1943-05-18 Manly Corp Fluid pressure device
US2335567A (en) * 1942-05-20 1943-11-30 Oilgear Co Reversible vane motor
US2411602A (en) * 1942-09-03 1946-11-26 Vickers Inc Pump for power transmissions
US2947320A (en) * 1954-11-08 1960-08-02 Robotyper Corp Convertible valve structure
US2826176A (en) * 1955-07-26 1958-03-11 United Shoe Machinery Corp Fluid motors for fastener inserting devices
US3152614A (en) * 1956-04-09 1964-10-13 Carls William Valve
US2955843A (en) * 1957-11-25 1960-10-11 Ford Motor Co Air suspension system having a cross flow control valve

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3381584A (en) * 1965-05-07 1968-05-07 Abegg & Reinhold Co Vane type rotary devices
US3450004A (en) * 1967-06-06 1969-06-17 Biasi Charles P De Auto-kinetic wheel or fluid motor
US3610272A (en) * 1968-07-05 1971-10-05 Blease Medical Equipment Ltd Valve block
US4052929A (en) * 1973-02-07 1977-10-11 Danfoss A/S Hydraulic control means, especially a steering means
US4331120A (en) * 1978-10-31 1982-05-25 Toyota Jidosha Kogyo Kabushiki Kaisha Device for controlling evaporative emission from an automobile
US4301832A (en) * 1980-05-19 1981-11-24 Smith Dale R Pressure converter valve
US20140216574A1 (en) * 2013-02-01 2014-08-07 Denso Corporation Relief valve
US10584561B2 (en) 2014-01-03 2020-03-10 Proserv Operations, Inc. Dirty fluid pressure regulator and control valve
US20170031371A1 (en) * 2015-07-27 2017-02-02 Proserv Operations, Inc. Dynamic variable orifice
US9880566B2 (en) * 2015-07-27 2018-01-30 Proserv Operations, Inc. Dynamic variable orifice
US10670155B2 (en) 2015-10-05 2020-06-02 Proserv Gilmore Valve Llc Latching poppet valve
US10487951B2 (en) 2016-01-22 2019-11-26 Proserv Operations, Inc. Non-interflow directional control valve
US10591076B2 (en) 2016-09-15 2020-03-17 Proserv Operations, Inc. Low friction hydraulic circuit control components
US10739796B2 (en) 2017-09-22 2020-08-11 Proserv Gilmore Valve Llc Pressure regulator with reconfigurable hydraulic dampening
US10633951B2 (en) 2017-09-22 2020-04-28 Proserv Operations, Inc. Pressure regulator with user selectable dampening
US11022226B2 (en) 2018-03-20 2021-06-01 Proserv Operations, Inc. Microfluidic valve
US11054050B2 (en) 2018-08-13 2021-07-06 Proserv Operations Inc. Valve with press-fit insert
US11713824B2 (en) 2018-08-13 2023-08-01 Proserv Gilmore Valve Llc Valve with press-fit insert
US11209096B2 (en) 2018-11-19 2021-12-28 Proserv Operations, Inc. Bilateral and throttling directional control valve
US11261982B2 (en) 2019-06-27 2022-03-01 Proserv Gilmore Valve Llc Pressure relief valve with bi-directional seat
US11686402B2 (en) 2019-06-27 2023-06-27 Proserv Gilmore Valve Llc Pressure relief valve with bi-directional seat
US11828370B2 (en) 2020-01-02 2023-11-28 Proserv Gilmore Valve Llc Check valve with conforming seat

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