US2641193A - Power transmission - Google Patents

Description

June 9, 1953 Filed Oct. 19. 1950 E. F. KLESSIG POWER TRANSMISSION 5 Sheets-Sheet 1 INVENTOR ERNST F. KLESSIG ATTORN EY Jun 9, 1953 E. F. KLESSIG 2,641,193

POWER TRANSMISSION Filed Oct. 19. 1950 3 Sheets-Sheet 5 INVENTOR ERNST F. KLESSIG CKMQM ATTORN EY Patented June 9, 1953 POWER TRANSMISSION Ernst F. Klessig, Berkley, Mich., assignor to Vickers Incorporated, Detroit, Mich., a corporation of Michigan Application October 19, 1950, Serial No. 190,958

This invention relates to power transmissions, and is particularly applicable to those of the type comprising two or more fluid pressure energy translating devices, one of which may function as a pump and another as a fluid motor.

This invention is more particularly concerned with a vane pump or motor construction adapted for use in hydraulic power transmission systems.

A form of pump in common use in the hydraulic power transmission field utilizes a rotor having a plurality of substantially radial vanes rotatable therewith and slidable relative thereto. The rotor is mounted within a chamber, the contour of which forms a vane track against which the outer ends of the vanes are adaptedto be maintained in contact. The chamber forming the vane track may comprise the inner portion of a vane track ring. The vane track is adapted to control the movement of thevanes and cooperates with the rotor in forming working chambers through which the vanes pass as the rotor turns. The external connection ports lead by passage means to the working chambers so as to form separated fluid inlet and outlet zones.

8 Claims. (Cl. 103-436) Some means in addition. to centrifugal force is' utilized to maintain the outer ends of the vanes in contact with the vane track, which is essential for efficient operation. One method has been to connect the high pressure side of the device to the inner ends of the vanes. However, a problem arises in maintaining the contact when there is no pressure available. When the device is utilized as a motor it is particularly important at starting operation that some slight force be employed for urging the vanes outward in contact with the track, otherwise leakage would occur around the outer ends of the vanes and cause free wheeling of the device. It is also important that contact be maintained as the.

vanes pass over the sections forming the separation between the inlet and outlet fluid zones. In addition, as the vanes pass through the high pressure zone of the device, there is a tendency for the vanes to separate from the track because A must contract and expand, they fatigue rapidly. In order to meet commercial operating requirements, the rotor size would have to be greatly increased to provide proper mounting area for the larger types of springs demanded. This is impractical when size, weight and cost are to be considered.

Where the individual coil spring type of construction is utilized the spring is continuously subjected to the full travel of the vane. Where the device is of the double throw type, i. e., each vane having two complete strokes per rotor revolu tion, and the rotor speed is in excess of 1000 R. P. M. it can be clearly seen that each spring is subjected to over 2000 full travel strokes of the vane each minute. The fatigue life of the coil spring is thus certain to be short.

It is therefore an object of this invention to provide in devices of this type an improved means of preloading the vanes into contact with the vane track.

It is a further object to provide preloading of the vanes into contact with the vane track by spring type of construction.

It is another object to provide bell crank members for the purpose stated which are pivotally connected at their central portions to the rotor and the arms of which by lever action transmit the motion of one vane to another complementary vane.

It is another object to provide members of the type and for the purposes mentioned which are resilient so as to produce the preloading of the vanes desired but arranged to produce the lever action required without significant bending action as the vanes travel through their full strokes.

It is still another object of this invention to provide a novel, economical means for selectively preloading the vanes in contact with the vane track which is efi'icient over a long useful life.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred form of the present invention is clearly shown.

of Figure 1.

Figure 4 is a sectional view taken on line 4-4 3 of Figure 1 and embodying a preferred form of the present invention.

Figure 5 is a sectional view taken on line 5-5 of Figure 1.

Figure 6 is a partial sectional view illustrating the overlapping relationship of the members which preload the vanes in contact with the vane track.

Figure '7 is a partial sectional view taken on line 'iT of Figure 5.

Referring now to Figure 1 there is shown a rotary vane pump or motor ill, the body of which comprises a right end housing l2, a left end housing M, and a central housing member'or cam,

ring it which is sandwiched between and suitably bolted to the end housing members. The right end housing 12 is provided with a flange member l8 having an external connection port 2n which registers with a fluid passage 22 in the housing E2. The passage 22 has two branches 24 and 26 (Figure 3) which terminate respectively in arcuately shaped fluid openings 28 and 3D. The

' openings 28 and so register respectively with a portion of a pair of diametrically opposed working chambers 32 and 34. (Figure 4).

The working chambers 32 and 34 are formed by the mounting of a rotor 36 within the'c'am ring it, the inner contour of which is generally elliptical in shape and forms a vane track indicated by the numeral 38. The rotor 36 is connected to a shaft to rotatably mounted and supported in bearings 3-2 and 44 completely in the right end housing [2, said rotor being spline connected at 4% to the mating spline of the shaft. A shaft seal 28 is provided and the shaft bore 50 may be drained through an external connection port 52 connected to the bore.

' Referring now to Figures 1 and 5, the left end housing member is provided with a flange member 54 having an external connection port 56 registering with a passage 59 in the housing member which leads to a recess 58. The open end of the recess is closed by the cam ring and rotor.

A side plate 6i} is floatably mounted in the recess to form a pressure chamber 62. The side plate 66 is adapted to be maintained in engagement against the cam ring [6 and in fluid sealing engagement with the rotor by means of pressure fluid delivered to the chamber. The side plate has a peripheral groove 64 connected to which are two diametrically opposed pairs of drilled passages 66 and 38 and 1D and 12. The side plate also has on the face thereof immediately adjacent to the rotor two arcuately shaped fluid openings l4 and T6. The drilled passages '86 and B8 are connected to the opening H while the drilled passages 15 and 12. are connected to the opening 76. The openings 14 and 76 are diametrically opposed and register with portions of the working chambers 32 and 34.

Means have been provided in the side plate 60 for connecting the high pressure side of the device to the pressure chamber 62 regardless of the direction of operation of the device. Thus there is provided a shuttle valve 77 mounted in a bore 79 connected to the pressure chamber 82 by a passage 8 l. The shuttle valve 11 is connected at one end thereof to the side plate groove 64 by a passage 83 and connected at its opposite end to that portion of the working chamber 32 which registers with the fluid opening 28 by a passage From the pressure chamber 62 pressure fluid is directed to the inner enlarged portions of the vane slots in the rotor, hereinafter described, by

4 means of a plurality of ports 81 extending completely through the side plate and which lead to a recess 89 in the rotor, the latter being connected to the enlarged slot portion 80. The opposite face of the rotor 36 is provided with a duplicate circular recess 89.

The rotor 36 is constructed with a plurality of substantially radially extending slots 78 having the aforementioned enlarged portions at their inner end. Slidably mounted in the slots 18 are vanes 32 substantially rectangular in shape, the outer ends of which are adapted to engage the vane track 38.

The construction of the device as herein described constitutes a balanced rotary vane device of the double throw type, the contour of the cam ring being substantially elliptical in shape and with two pairs of diametrically opposed fluid openings registering with the working chambers formed. Each vane will be retracted completely twice during one rotor revolution. Each vane on a retracting stroke has a complementary vane which is adapted to be urged outwardly in contact with the vane track during a corresponding outward stroke. In the device illustrated which is provided with twelve slots and vanes, the complementary pairs of vanes are 90 degrees apart although it should be understood that in a single throw unit the spacing will be in a triple throw 69, etc.

Means for urging and maintaining the outer ends of the vanes in contact with the vane track 322 in addition to pressure fluid directed to the inner ends of the vanes has been provided by roekably or pivotally mounting bell crank members 90 in the-rotor. As shown in Figures 4 and 6 the bell crank members 90 are connected at their central portions to a plurality of pivot pins 92 which are loosely, rotatably mounted in bores 94 arranged in circular formation and extending through the rotor, said bores opening at opposite ends to-the recesses. Each bell crank member is coiled at its central portion indicated by the numeral 93 so that it may be pivotally connected at the coiled portion to a bushing 98 having a flange I00 which may be suitably riveted to the end portion of the pivot pin. The two arms of each member indicated by the numerals I02 and I04 are on different planes to provide a proper staggered relationship of the members around the rotor and permitting free movement of the same. The coiled section is thus loosely pivoted between the surface surrounding the pivot pin bore and the flange M0.

The arms of the bell crank members illustrated lie between the planes containing the axially spaced edges of the vanes. They also underlie the inner endsof all intermediate vanes within the span between complementary vanes. The arms of the members are bent to avoid the intermediate vanesvan'd at their ends to engage the inner ends of complementary vanes and resiliently load said vanes in engagement with the track. There is thus no interference with intermediate vanes with which the members do not cooperate. As the arms of each member are on different planes the alternating arms will be properly staggered around the rotor for efficient continual lever action without interference of adjoining members.

Each vane is urged outwardly by the opposing arms of two bell crank members on opposite sides of the rotor while the complementary vane which is 90 degrees apart therefrom is urged in contact with the vane track by the remaining two opposing arms of the said two bell crank members.

. track thereby preloading said vane.

The arms of the bell crank members are of predetermined resiliency .so that" when the outer portions are placed under the vanes that the vanes will be urged into contact with the vane However, the arms should preferably be of sufiicient strength. so that the motion of a vane on an inward stroke may be transferred by the one arm by lever action to the other arm so as to urge the complementary vane outwardly in contact with the track without substantial flexure of the arms.

In operation when the device is operated as a motor and pressure fluid is directed to the external connection port 26, pressure fluid is conducted by the passage 22, branch passages 24 and lit and fluid openings 26 and 28 to that portion of the working chambers 32 and 34 registering with said openings. Pressure fluid acting on the outer portions of the vane causes counterclockwise rotation of the rotor and fluid will be displaced from the remaining portions of the working chamber as the vanes pass therethrough by means of the openings M and T6, drilled pastions 8i? of the vane slots 18 by means of the side with the vane track 38.

sure is directed to the external connection plate port til and recess 89 in the rotor 36. Pressure fluid acting at the inner ends of the vane slots will urge the outer ends of the vanes in con For reversal, presjport and fluid is conducted to that portion of 1 the working chambers registering with the openings it and 7 3 in the side plate 60. The passage of fluid is follows, external connection port 56, age groove t l, drilled passages 65, 58, Hi l2 and the openings 74 and it in the side plate Pressure fluid is conducted to the pressure chamber 62 from the side plate groove by means "of passage 33, shuttle valve 1'! and passage 8!. From the pressure chamber pressure fluid is dito the inner ends of the vane slots by the tion pos iii in the side plate Gil. The side plate 60 will be maintained in engagement against a perring it? and in fluid sealing enhit with the rotor by means of pressure nrecl'ed from the high pressure side of the device to the pressure chamber 62. No matter what the direction of the operation of the device, the high pressure side of the device is constantly onnected to the pressure chamber by reason of the shuttle valve and associated passages in the side plate.

At starting and at times when there is no pres" sure available the bell crank members 90 will maintain the outer ends of the vane in'contact with the vane track. In addition, they will supply the slight additional force required to prevent the vanes separating from the track as they pass through the inlet zones. As the vane track causes vane to shift inwardly, at the start of an inward stroke, a complementary vane 90 degrees is adapted to be starting an outward stroke.

The of the opposing members which are i forced inwardly will. transfer by lever action the arms of the members. This outward motion of inward motion of its complementary vane. to produce an outward motion of the remaining 6 the remaining arms will cause an outward stroke of the complementary vanes.

It should thus be noted that the bell crank members perform two functions. They serve to preload the vanes in contact with the vane track. In addition, they cause the inward motion of the vanes to be transferred to complementary vanes on a corresponding outward stroke. As the members are loosely pivotally connected at their central portions, this motion is transferred by lever action. Without substantial ilexure they are not therefore subject to the short fatigue life of the individual coil spring construction.

It should be noted that no positive connection of the arms to the vanes is necessary. Another feature is that the rotor does not have to be increased in size to providemounting space for the bell crank members. In addition the length of the slot does not have to be increased as in the individual coil spring type of construction. Instead the mounting recess may be constructed starting at substanitally the middle of the vane slots. This recess will not only serve to provide mounting space for the members but in devices constructed as illustrated the recess serves to con nect the pressure ports in the side plate to the under portions of the vanes thereby connecting the pressure chamber to the vane slots.

As the pins for the members are mounted between the vane slots and on a level above the enlarged portions of the vane slots there will be sufficient space for the full travel of the lever arm. The downwardly curved portion of the arm prevents interference with vanes immediately adjacent to the pins and with which the arm is not adapted to cooperate. As the arms of the members are on two planes there will be no interference between immediately adjacent arms of adjacent members.

While the form of embodiment of the invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which follow.

What is claimed is as follows:

1. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a vane track of non-circular contour and a rotor mounted within the track having a plurality of generally radial slots, each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising a plurality of bell crank members each of which is pivotally mounted at its central portion on the rotor between a pair of complementary vanes and outwardly of:

the innermost ends of the vane slots, the arms of each member underlying the inner ends of all intermediate vanes Within the span between complementary vanes and the outer ends of the arms engaging the inner ends of complementary vanes, said arms of each member being on two planes to avoid interference with the arms of adjacent members and being flexible to resiliently load the complementary vanes in engagement with the track, and said arms being of sufficient strength to transfer by lever action without substantial flexure the inward motion of one vane to its complementary vane to cause the outward stroke of said vane.

'2. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a rotor chamber, a rotor mounted within the chamber having a plurality of vane slots and each slot having a vane slidably mounted therein, the contour of the chamber forming a vane track against which the outer ends of the vanes are adapted to be constantly urged and said track causing complete inward strokes of each vane during a rotor revolution, each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising a plurality bell crank members each of which is pivotally mounted at its central portion on the rotor between a pair of complementary vanes and between the innermost ends of the vane slots and the periphery of the rotor, the arms of each member being bent to avoid interference with intermediate vanes between complementary vanes and at their ends to engage the inner ends of complementary vanes, said arms of each memberbeing on two planes to avoid interference with the arms of adjacent members and being flexible to load the complementary vanes in engagement with the track, and said arms being of sufficient strength to transfer by lever action without substantial flexure the inward motion of one vane to its complementary vane to cause the outward stroke of said vane.

3. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a vane track of non-circular contour and a rotor mounted within the track having a plurality of generally radial slots. each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising means forming recesses on opposite faces of the rotor, a plurality of pivot pins mounted in the rotor the opposite ends of which extend into the recesses, one between each pair of complementary vanes, and a bell crank member on each end of each pin,

the members being pivotally connected at their central portions on the ends of said pins, the arms of each member underlying the inner ends of all intermediate vanes within the span between a pair of complementary vanes and the outer ends of the arms engaging the inner ends of a pair of complementary vanes, said arms of each member being on two planes to avoid interference with the arms of adjacent members and being flexible to resiliently load the vanes in engagement with the track, and said arms being of sufiicient strength to transfer by lever action without substantial flexure the inward motion of one vane to its complementary vane to cause the outward stroke of said vane.

4. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a vane track of non-circular contour and a rotor mounted within the track having a plurality of generally radial slots, each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising a plurality of bell crank members each of which comprises a single strand of wire coiled at its central portion to form the arms of the member in two planes, a plurality of pivot pins mounted in the rotor the ends of which extend from the rotor, one

. between each pair of complementary vanes, and

a bell crank member pivotally mounted on each end of each pin, the members being mounted by their coiled portions on the ends of said pins, the arms of each member underlying the inner ends of all intermediate vanes within the span between complementary vanes and the outer ends of the arms engaging the inner ends of complementary vanes, said arms being flexible to resiliently load the complementary vanes in engagement with the track and being of sufiicient strength to transfer by lever action without substantial flexure the inward motion of one vane to its complementary vane to cause the outward stroke of said vane.

5. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a vane track of non-circular contour and a rotor mounted within the track having a plurality of generally radial slots, each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising means forming recesses on opposite faces of the rotor, a plurality of pivot pins mounted in the rotor the opposite ends of which extend into the recesses, one between each pair of complementary vanes, a plurality of hell crank members on opposite sides of the rotor, one on each end 01' each pin, each member comprising a single strand of wire coiled at its central section to form the arms in two planes and being pivotally connected by its coiled portion on the end of the pin, and a flange on the end of each pin retaining the member on the pin, the arms of each member being bent to avoid interference with intermediate vanes within the span between complementary vanes and at their ends to engage the inner ends of complementary vanes, said arms being flexible to resiliently load the complementary vanes in engagement with the track and. of sufiicient strength to transfer by lever action without substantial flexure the inward motion of one vane to its complementary vane to cause the outward stroke of said vane.

6. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a vane track of non-circular contour and a rotor mounted within the track having a plurality of generally radial slots, each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising a plurality of bell crank members each 01' which is pivotally mounted at its central portion on the rotor between a pair of complementary vanes and outwardly of the innermost ends of the adjoining vane slots, said arms engaging at their outer ends the inner ends of a pair of complementary vanes, said arms of each member being on two planes to avoid interference with the arms of adjacent members and being flexible to resiliently load the complementary vanes in engagement with the track, and said arms being of suificient strength to transfer by lever action without substantial fiexure the inward motion of one vane to its complementary vane to cause the outward stroke of said vane.

7. In a fluid pressure energy translating device of the rotary vane type comprising a housing having a vane track of non-circular contour and a rotor mounted within the track having a plurality of generally radial slots, each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising a plurality of bell crank members each of which is pivotally mounted at its central portion on the rotor between a pair of complementary vanes and outwardly of the innermost ends of the vane slots, the arms of each member lying between the planes containing the axially spaced edges of the vanes and being bent to avoid interference with the inner ends of all intermediate vanes within the span between complementary vanes and at their outer ends to engage the inner ends of complementary vanes, said arms being flexible to resiliently load the complementary vane in engagement with the track, and said arms being of sufficient strength to transfer by lever action without substantial fiexure the inward motion of one vane to its complementary vane to cause the outward stroke of said complementary vane.

8. In a fluid pressure energy translating device of the rotary vane type comprising a, housing having a vane track of non-circular contour and a. rotor mounted Within the track having a plurality of generally radial slots, each slot having a vane slidably mounted therein the outer end of which is adapted to be constantly urged against the track, said track causing complete inward strokes of the vanes during a, rotor revolution and each vane on an inward stroke having a complementary vane adapted to be on an outward stroke, that improvement comprising a plurality of bell crank members each of which is pivotally mounted at its central portion on the rotor between a pair of complementary vanes and between the innermost ends of the adjoining vane slots and the periphery of the rotor, said arms engaging at their outer ends the inner ends of a pair of complementary vanes and said arms being bent to underlie the inner ends of all intermediate vanes within the span between complementary vanes, said arms being of sufiicient strength to transfer by lever action without sufficient flexure the inward motion of one vane to its complementary vane to cause the outward stroke of said complementary vane.

ERNST F. KLESSIG.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,284,083 Flinn Nov. 5, 1918 1,303,745 Vogan May 13, 1919 1,732,871 Wilsey Oct. 22, 1929 1,898,914 Vickers Feb. 21, 1933 1,989,900 Vickers Feb. 5, 1935 2,444,165 Lauck June 29, 1948 2,469,510 Martinmaas, Jr. May 10, 1949 2,544,988 Gardiner et a1 Mar. 13, 1951 2,556,313 Adams et al June 12, 1951 2,588,342 Bidwell Mar. 11, 1952 FOREIGN PATENTS Number Country Date 499,923 France 1919

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