US3099964A

US3099964A - Vanes for rotary vane machine supported in balance and in stability and in less friction

Info

Publication number: US3099964A
Application number: US792001A
Authority: US
Inventors: Eickmann Karl
Original assignee: Individual
Current assignee: Individual
Priority date: 1958-03-13
Filing date: 1959-02-09
Publication date: 1963-08-06
Anticipated expiration: 1980-08-06

Description

Aug. 6, 1963 K. EICKMANN 3,099,964

VANES FOR ROTARY VA MACHI SUPPORTED IN BALANCE AND IN STABI Y AND LESS FRICTION Filed Feb. 9, 1959 8 Sheets-Sheet 1 HHHHHH INVENT A KARL ElC/(M/INA/ w w w m na R NE Y5 g 1963 K. EICKMANN 3,099,964

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VANES FOR ROTARY VANE MACHINE SUPPORTED IN BALANCE AND IN STABILITY AND IN LESS FRICTION Filed Feb. 9, 1959 8 Sheets-Sheet 4 Fig. 36 v Fig. 55

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VANES FOR ROTARY VANE MACHINE SUPPORTED IN BALANCE AND IN STABILITY AND IN LESS FRICTION Filed Feb. 9, 1959 8 Sheets-Sheet 5 Fig. 42

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VANES FOR ROTARY VANE MACHINE SUPPORTED IN BALANCE I AND IN STABILITY AND IN LESS FRICTION Filed Feb. 9, 1959 8 Sheets-Sheet 6 Fig. 50

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IN VENTOR.'

KARL E/(lrM/uwv A TFO RNEYS Aug. 6, 1963 K. EICKMANN 3,099,964

VANES FOR ROTARY VANE MACHINE SUPPORTED IN BALANCE AND IN STABILITY AND IN LESS FRICTION Filed Feb. 9, 1959 8 Sheets-Sheet 8 Fig.6?

INVENWKI KARL Em KMA/VA/ ATTOR'VEYS United States Patent 3,699,964 VANES FOR ROTARY VANE MACmE S U?- PORTED 1N BALANCE AND IN STABEITY AND IN LES FRICTEON Karl Eickmann, Talmuhle, Kreis Calw, Germany Filed Feb. 9, 1959, Ser. No. 792,001 Claims priority, application Japan Mar. 13, 1953 22 Claims. (Cl. 103136) This invention relates to vanes of rotary vane machines and more particularly to such vanes which are provided with extended slide portions -for stabilizing the movement of the vanes and eliminating the tilting of the vanes in their respective guide slots during operation. These vanes are further provided with recesses into which a pressure medium may be directed so as to produce counteracting forces to those exerted by the pressure medium tangentially to the rotor and normal to the lateral vane wall as well as those exerted radially outwardly against the bottom vane wall. In this way, the vanes may be stably supported in their respective slots and the tangential force causing undesired tilting may be completely or at least partially counterbalanced. Heretofore, various vane constructions for rotary vane machines have been used, although in such constructions there has been undesirable tilting of the vane due to the unilateral tangential force exerted thereagainst. Such tilting causes friction and wear along the lower trailing edges of the vane and slot as well as along the upper leading edges of the vane and slot. Previously, ttle importance was attached to this tilting and the resultant friction and wear, since rotary vane machines operating at low eificiency were considered adequate.

A typical rotary vane machine is set forth in British Patent No. 744,446 (Feb. 8, 1956) In that case, a rotary fluid-driven engine, either a motor or pump, is provided with vanes which slide in slots located in the rotor and are enclosed by a casing ring, thereby defining compression cells. Each cell during rotation of the machine as a motor admits a fluid or pressure medium under pressure as the cell increases in volume and releases the fluid or medium as the cell decreases in volume, while in acting as a pump the cell draws in the fluid or pressure medium by suction as the cell increases in volume and expels the fluid or medium under pressure as the cell decreases in volume. Recently, however, the elimination of tilting and friction of the vane has become increasingly important where the machine is required to operate at high efdciency and with minimum frictional losses as is the case with conventional unadjustable gear transmission machines.

It is an object of the present invention to provide a vane construction for rotary vane machines having means for stabilizing the vane during rotation and tor counterbalancing the forces of the pressure medium acting on the vane, whereby to permit tree floating travel of the vane in the guide slot and reduce friction and wear of the vane passing against adjacent parts.

Other and further objects will become apparent from a study of the specification and accompanying drawings.

It has been found, in accordance with the present invention, that frictional forces and tilting forces of the vane as well as centrifugal forces and forces acting on the bottom side of the vane may be more or less completely balanced by corresponding counteracting forces. Thus, stabilized support of the vane during operation will reduce friction to a minimum and these counterbalancing forces will prevent any overloading that would otherwise cause undue wear.

Specifically, in accordance with the preferred embodiment of the invention, the vane assembly is divided into 3,099,964 Patented Aug. 6, 1963 a vane and a slide element. The slide element is located in a channel provided along the top edge of the vane and can rotate to a limited extent about its longitudinal axis in said channel. The top surface of the slide element is constructed to smoothly abut the inside surface of the casing ring against which it slides during rotation. Recesses are provided in the top surface of the slide element into which the pressure medium of the machine may be passed, so as to act against both the slide element and the casing ring and prevent friction. In acting against the slide element and easing ring, a force is provided which completely or at least partially counter-balances the outward radial forces exerted against the bottom of the vane in the slot and in turn transmitted radially outwardly to the slide element. In order to accomplish this counterbalancing by means of so called pressure fields created in the slide recesses and also to stabilize vane support, the slide element is preferably constructed oi greater width than the vane. Accordingly a larger area of contact with the casing ring surface is provided which improves the supporting stability of the slide element.

Moreover, in normal rotary vane machine operation, the pressure medium acts on the vane in one direction when the cell or intervane space acts as a compression cell or interva-ne space and in the opposite direction when the cell or inter-vane space acts as a suction cell or intervane space. The vane travels more or less radially out wardly within the vane slot provided in the rotor during rotation of the machine about one half of the axis of rotation and then more or less radially inwardly within the slot during rotation about the other half of the cycle. During such operation in conventional rotary vane machines, the ressure medium acts on the vane tangentially to the rotor, causing unilateral pressure against the vane during its travel within the slot. The friction produced by this one-sided force against the vane is considerable and consequently reduces the efiiciency of the machine.

To overcome these drawbacks of conventional rotary vane machines, recesses are provided in the lateral sur faces of the vane into which the pressure medium may be transmitted by means of bore passages or channels in the vane. These va-ne recesses are arranged in such a manner that the force or pressure fields produced by the pressure medium therein may be utilized to counterbalance the unilateral tangential torce acting against the opposite side of the vane. Upon reaching this state of counterbalance, the vane substantially floats in the guide slot.

Thus, in a construction according to the invention, metal contact between the vane and guide slot is almost completely avoided. The unilateral force acting on one side of the vane is transmitted to the slot as well as to the rotor of the machine, and by means of the above construction creates counterbalancing pressure fields. Consequently, instead of metal acting on metal, the pressure medium acts on metal, and the vane is free to float in the guide slot with a minimum of triction and wear. Although internal friction caused by the molecules in rats tion in the fluid may still be present, this friction is comparatively negligible.

The invention is further illustrated by the accompanying drawings in which:

FIG. 1 is a partial sectional view of a rotary vane machine taken along the line 11 of FIG. 2 and along the line 1-1 of FIG. 3.

FIG. 2 is a partial sectional view taken along the line 22 of FIG. -1 showing the vane recesses.

FIG. 3 is a partial sectional view taken along the line 3-3 of FIG. 1 showing the slide element.

FIG. 4 is a side view showing an embodiment of the vanes of a rotary vane machine according to the invention.

FIG. 5 is a sectional view taken along the line 5-5 of FIG. 4.

FIG. 6 is a top plan view of the vane in FIG. 4, the view illustrating the forces acting on the vanes in tangential direction to the rotor, and the balancing pressure fields counteracting said forces.

FIG. 7 shows a partial section taken along the line 6-6 of FIG. 4.

FIG. 8 is an enlarged view of a partial section taken along the line 2-2 of FIG. 1, showing the end portion of the vane positioned in the slot defined by the side-walls of the rotor, the view illustrating the acting force in tangential direction and the balancing pressure fields in counter direction where the vane has moved slightly outwardly in a radial direction within the slot.

FIG. 9 is a sectional view similar rto FIG. 8 showing the vane further outwardly positioned in a radial direction the slot of the rotor and indicating the consequent existence of greater forces.

FIG. 10 is an enlarged view of a partial section taken along line 3-3 of FIG. 1 showing the force of the vane and of the slide element produced in a radial direction and the balancing of these forces by means of corresponding counter pressure fields.

FIG. 11 shows an embodiment of the vane slide ele ment.

FIG. 12 is a sectional view taken along the line 12-12 of FIG. 13.

, FIG. 13 is a top view of the vane slide element of FIG. 11.

FIG. 14 shows an embodiment of the assembly of the vane and the vane slide element.

FIG. 15 is a sectional view taken along the line 15-15 of FIG. 14.

: FIG. 16 is a top view of FIG. 14.

FIG. 17 is a sectional view of a further embodiment of the rotary vane machine illustrating additional mechanical details.

FIG. 18 is a partial sectional view taken along the line 18-18 of FIG. 17.

FIG. 19 is a sectional view of a further embodiment of the rotary vane machine.

FIG. 20 is a partial sectional view taken along line 20- 20 of FIG. 19.

FIG. 21 is a further embodiment showing the vane slide element comprising two separate members.

FIG. 22 is a sectional view taken along the line 22-22 of FIG. 21.

FIG. 23 shows a rotating part of the vane slide element of FIG. 21.

FIG. 24 is a sectional view taken along the line 24-24 of FIG. 23.

FIG. 25 shows a sliding member of the slide element in FIG. 21 having balancing pressure field recesses.

, FIG. 26 is a sectional view taken along the line 26-26 of FIG. 25.

FIG. 27 shows a further embodiment of the vane slide element comprising two separate members.

FIG. 28 is a sectional view taken along the line 28-28 of FIG. 27.

- FIG. 29 shows a rotating member of the vane slide element of FIG. 27.

FIG. 30 is a sectional view taken along the line 30-30 of FIG. 29.

FIG. 31 is a top view of the sliding member of FIG. 27

FIG. 32 is a sectional view taken along the line 32-32 of FIG. 31.

FIG. 33 is another embodiment :of the vane having a slide element comprising two separate members.

FIG. 34 is a sectional view taken along the line 34-34 of FIG. 33.

FIG. 35 is a side elevation view of the vane shown in FIG. 33 with the slide element removed.

FIG. 36 is a sectional View taken along the line 36-36 of FIG. 35.

FIG. 37 is a side view of the separate rotating member of the vane slide element of FIG. 33.

FIG. 38 is a sectional view taken along the line 38-38 of FIG. 37.

FIG. 39 is a side view of the separate sliding member of the vane slide element of FIG. 33.

FIG. 40 is a sectional view taken along the line 40-40 of FIG. 39.

FIG. 41 is a side elevation view showing another embodiment similar to that of FIG. 33.

FIG. 42 is a sectional view taken along the line 42-42 of FIG. 41.

FIG. 43 is a side elevation view of the vane of FIG. 41 with the slide element removed.

FIG. 44 and FIG. 45 show sectional views taken along the line 44-44 and 45-45 of FIG. 43, respectively.

FIG. 46 and FIG. 47 show a side view and sectional view of the rotating member of the vane slide element of FIG. 41, respectively.

FIG. 48 and FIG. 49 show a side view and a sectional view of the sliding member of the vane slide element of FIG. 41, respectively.

FIG. 50 is an embodiment of the vane in which the rotating member of the vane slide element is covered by a separate bearing cover.

FIG. 51 is a sectional view taken along the line 51-51 of FIG. 50.

FIG. 52 is a side elevation view of the vane shown in FIG. 50 with the slide element removed.

FIG. 53 and 54 show sectional views taken along line 53-53 and 54-54 of FIG. 52, respectively.

FIG. 55 and FIG. 5 6 shows a side elevation view of the bearing cover and a sectional view taken along the line 56-56 of FIG. 55, of the embodiment in FIG. 5 0 respectively.

FIG. 57 and FIG. 58 are a side view and -a sectional view of a pin in FIG. 50.

FIG. 59 and FIG. 60 are a side view and a sectional view of the rotating member of the vane slide element of the embodiment in FIG. 50, respectively.

FIG. 61 and FIG. 62. are a side View and a sectional view of the sliding member of the vane slide element of the embodiment shown in FIG. 50, respectively.

FIG. 63 is a side View of the vane and slide element showing a 'further means for receiving the slide element in the vane.

FIG. 64 is a cross section along the line 64-64 of FIG. 63.

FIG. 65 is a side view of the vane shown in FIGS. 63 and 64 with the slide element removed.

FIG. 66 is a cross section along the line 66-66 of FIG. 65.

FIG. 67 is a side view of another embodiment of the invention showing adjustable vane recesses for conrespondingly adjusting the balancing pressure fields.

FIG. 68 is an enlargement of a cross-sectional view taken along the line 68-458 of FIG. 67 illustrating the manner of adjustment of the vane recesses.

Referring to the drawings, in FIGS. 1, 2, and 3, 1 represents a control shaft of a rotary vane machine, 2 is the rotor, and 3 represents bores guiding radially outwardly and inwardly the pressure medium to and from the slot space below the vane through the control shaft. 4 is a channel guiding outwardly the pressure medium from the rotor during each revolution of the machine. 5 is a shaft driving the rotor. 6 is a casing ring. 7 and 8 are extended portions of the vane slot defined by the side walls of the rotor. 7a and 8a are pressure medium chambers located radially in the vane slot above the vane. 9 and 16 are side-covers sealing axially and radially the side wmls of the rotor. 11 are vanes of the rotary vane machine and '12 is a slide element thereon. 13 is an extended rotatingmernber of the slide element adjacent the side wall. 14 is an extended portion of the vane located along the side wall and rotating therewith. 15 and 16 we U-shaped portions located on the extended portions of the vane with bucklings to prevent the slide positioned therewithin from falling out of the vane. 17 and 18 are balancing pressure recesses provided in the vane. 17:: md 18a are corresponding balancing pressure recesses provided separately in the vane. 27 is a balancing pressure recess in the slide. 28 is a pressure medium chamber located radially and inwardly of the vane. 29 is a passage in the rotor for guiding the pressure medium into and out of the vane cells or intervane spaces. 36 and 39 are two adjacent vane cells or intervane spaces. These cells or intervane spaces are the vane chambers of the rotary vane machine.

In FIGS. 4, 5, 6 and 7, 11 is the vane, 14 is the extended side portion of the vane adjacent the side wall of the rotor. 15a is an inner bent buckling along the top edge of the vane preventing the slide from falling out of its vane seat. 17, 17a, 13, and 13a are balancing pressure recesses in the vane. 19 and 29 are additional balancing pressure recesses in the vane, opposite corresponding balancing pressure recesses 19a and 26a, not shown. 23 is a bore channel guiding the pressure medium into the balancing pressure recess 19. 21, 22, 2d, 25, and 26 are bore channels for correspondingly guiding the pressure medium to balancing pressure recesses 29, 26a, 18a, 18, and 17. 31 shows the working medium under pressure acting on the vane in the direction of the arrow c. 32 and 33 show the balancing pressure fields created in the vane recesses on the opposite side of the vane and the working direction of the counteracting pressure in the balancing pressure fields.

In FIGS. 8, 9 and 10, 2 is the rotor. '11 is the vane. 12 is the slide element; 6 is the casing, and 10 is the side wall sealing cover. 40 and 42 are radial pressure chambers inwardly to the vane, and 45 is a radial pressure chamber outwardly to the vane while 46 is a buckling of the vane. 39 is a vane cell or intervane space. 33 and 34 show the working medium under pressure acting on the vanes in different radial positions. 32, 35, and 36 show the pressure medium in the balancing pressure recesses counteracting the working pressure. 44 and 38 are widened slide ends providing a stabilized support for the slide. 6 shows the pressure medium acting radially and outwardly on the vane. 37 shows the balancing pressure field created in the slide element recesses which counteracts the pressure in 46.

In FIGS. 11, 12 and 13, 51 and 52- are rotating members of the slide element extended to fit adjacent the side wall of the rotor. 6 is the sliding surface of the sliding element adapted to slide along the casing ring. 53 is a balancing pressure recess provided in the slide element.

In FIGS. 14, l and 16, 11 is the vane and 15 and 16 are extended side portions of the vane, which are fitted into the side walls of the rotor defining the slots, and are inwardly bent to prevent the slide element from falling out. 56 is the sliding member of the slide element and 53 is a balancing pressure recess. 51 and 52 are rotatable extended portions of the slide element in the extended parts of the vane.

In FIGS. piston machine and 17, 18, 19 and 20, 2 is a rotor of the rotary 6 is the casing ring. 54 and 55 are slide sealing walls. '11 is an embodiment of the vane and 12 is a slide element. 60 is the rotating member of the slide element. 57 and 56 are guide rings urging the vanes radially and outwardly. 63 is a roller rotating over

rings

56 and 57 and 61 is a pressure spring forcing the slide element against the casing. 62 is a spring case surrounding spring 61 to prevent the spring from becoming dislodged, and transmitting the spring pressure to roller 63. 58 and 59 are sliding shoes fitted radially within the vane and are slidable on guide rings 56, 57. In this embodiment of the invention, radial projections are located on

shoes

58, 59 to prevent the shoes from axial movement between guide rings '56, 57 and

side walls

54, 55.

In FIGS. 21, 22, 2 3, 24, 25, 26, 27, 28, 29, 30, 31, and 32, 6'5, 66, 69, and 76 are rotating members of bipartite slide elements which permit the slides to rotate in the vanes. 64, 67, 68, and 71 are the sliding members of various types of bipartite slide elements. The slide elements rotate with these sliding members passing along the casing ring. 77 76, 74, and 73 are balancing pressure recesses provided in the slide elements. 72 and 75 are grooves in the sliding members for fitting therein the rotating members upon joining the two slide members together.

In FIGS. 33 to 40, 78 is a vane, 79 is a rotating member of the vane slide element and 80 is a sliding member of the slide element. 81 is a bore in the vane for supporting the rotating member of the slide element and 82 is a slot provided in the top face outwardly to the bore and radially to the vane. '83 is a bore provided in the sliding member of the vane slide element to fit therein the rotating member of the slide element.

In FIGS. 41 to 49, 84 is a vane, '85 is a rotating member of the slide element and 86 is a sliding member of the slide element. 87 is a bore provided in the vane to pivot the rotating member of the slide element, and 88 is a bore in the sliding member of the slide element for insertion of the rotating member.

In FIGS. 50 to 62, S9 is a vane, 90 is a rotating member of the vane slide element and 91 is a sliding member of the slide element. 92 is a bore provided in the vane to pivot the rotating member of the slide element. 93 is a groove provided above bore 92 along the extended vane portion radially to the wane for securing bearing cover 94. 95 and 96 are pin holes provided on the vane and the bearing cover for insertion of a pin 97 to connect vane 89 and bearing cover 94.

In FIGS. 63 to 66, 98 is a vlane, and the slide element comprises a rotating member 99 and a sliding member 160. 101 is a slot provided at the side end extension of the vane for supporting the rotating member of the slide element.

In FIGS. 67 and 68, 102 is the vane, 193 is the sliding member of the slide element, and 104- is the rotating member. 105 is the enclosing ring, 106 is the side Wall of the rotor, and 107 is the sealing cover of the side wall of the rotor. 108 is the rotor. 109 is the balancing pres sure recess provided on the side face of the vane and 110 is the sealing plate sealing from below the balancing pressure recesses. 111 is the pin fixing the sealing plate on the side face of the guide slot and rotor side wall. 113 is the conduit connecting the balancing pressure recess to the vane cell on The invention is more In FIGS. 1, 2, :and 3, the disposition of the vanes and slide elements in the rotary vane machine and the position of the balancing pressure recesses are shown. Vanes 11 slide in

radial guide slots

8 and 7 provided in rotor 2 and revolve together with the rotor. The rotary vane machine is enclosed by easing ring 6 and upon rotation vanes 11 are thrown radially outwardly by centrifugal and other forces, so that slide element 12, positioned on the top portion of the vane abuts the inside surface of casing ring 6 and slides along the casing ring.- In this way variable volume working cells are formed between casing ring 6, vanes 11 and slide elements 12, and side covers 9, 101 sealing axially and radially the rotor and side walls. During each revolution of the rotor, vanes 11 and side elements 12 travel radially inwardly and outwardly, so that the capacity of working cells or intervane spaces is increased and decreased accordingly. Two adjacent working cells or intervance spaces are shown in

positions

30 and 39 in FIG. 3. These cells or intervane spaces take up the working medium by means of distribution shaft 1 through the passages 29 during one half of the cycle and force the medium out through another passage of the distribution shaft 1 during the fully described by the followthe opposite side of the vane.

second half of the cycle. The rotor is driven by driving shaft 5, and the pressure medium leaves the rotor through bores 4. Passing through channels -3, the pressure medium enters slot chamber 2 8 radially below the vane through the distribution shaft. In these slot chambers, the pressure medium acts on the vane bottom forcing the vane radially outwardly. The vanes are shorter than the length of the slots located in the side walls or are provided with radial bores or slots, so that the pressure medium may either flow radially and outwardly along the lateral ends of the vanes, or may flow through the radial bores in the vanes, thereby reaching

chambers

7a or 8a, located radially Within the slots and above the vanes. An essential feature of (the invention concerns the passage of the pressure medium as from

chambers

7a, 8a into the balancing pressure recesses 27 provided in slide elements 12. In these balancing pressure recesses of slide element 12, a pressure field is produced and the pressure medium is directed radially inwardly, toward the vanes to counteract the radial outward pressure in slot chamber 28, and the centrifugal force acting on vane 11. This counteracting field completely balances the pressure force on the vane bottom from chamber 28 as well as the acting pressure force and centrifugal force, so that the vane in radial direction is completely free from or is only slightly effected by the hydraulic pressure force, acting pressure force, and centrifugal force. Even when the pressure of the medium is very high, the vanes are pressed radially and inwardly by said sliding element pressure field, so that compression between the vane and the casing ring or between the slide and the casing ring does not occur. Any overloading is therefore automatically prevented.

Where the rotary vane-machine serves as a motor with pressure medium revolving in the direction of arrow B, as shown in FIG. 3, vane 11 is forced by the working pressure in the cell 30 to rotate the rotor in the direction of arrow B. The pressure medium passing through

bores

23, 21 and 25, 26 in the vane, enters the balancing pressure recesses 20, 19 and 18, 17 from the cell 30. Consequently, the balancing pressure recesses 17, 18 and 19, 120 positioned in the extended side portion of the vane within the slot of the rotor are effected by similar pressure on the other side of the vane ahead of cell 30, and the pressure in these balancing fields is directed oppositely to the pressure in the direction of arrow B in cell 30, thus balancing completely or partially the working pressure in the direction of arrow B. In this Way, pressure load of vanes 11 within the slots is reduced completely or partially, and the vane travels freely in the pressure medium between the walls of the slot. While the balancing pressure recesses have been divided into 17 and 18, many balancing pressure recesses may be used so as to increase or decrease in any desired manner the pressure of the balanced pressure field in accordance with the degree of radial travel of the vane.

Contrastly, where the rotary vane machine serves as a pressure pump rotating in the direction of arrow B, the medium pressure is produced in cell 39, exerting a tangential pressure on vane 11 in the direction of arrow A. This pressure is balanced by the balancing pressure fields created in

recesses

17a, 18a, 19a, and 20a. The pressure medium flows to the balancing

pressure recesses

17a and 18a through bores 24 and 24a and to the balancing pressure recesses 19a and 20:: through bores 22 and 22a. This action of force is applicable similarly to all vanes 11 and slide elements 12 in corresponding positions of the rotor.

By extending considerably the vane ends 14 into

slot chambers

7, 8 a space is produced which is sufiiciently large for the balancing pressure fields created within the vane to balance the tangential pressure acting on the vane to any desired extent by bending over edges 15a, 16a of the vane, slide elements 12 cannot become dis- 8 lodged, as rotating member 13 is inserted below the bent portions of the vane.

FIGS. 4, 5, 6 and 7 show the recesses creating the balancing pressure fields counteracting the tangential force against the vanes; the disposition of bores guiding the pressure medium into the balancing pressure fields; the working pressure acting on the vanes; and the pressure in the balancing pressure recesses acting upon the vanes. Vane 11 has extended portions 14 with which it is fitted in the side walls of the rotor. An essential feature of the invention comprises providing in extended portions 14 recesses such as 17, 18', 19, 20, 17a, 18a, 19a and 20a or many further recesses suitably disposed for receiving the pressure medium therein. The pressure medium acting upon the opposite face of vane 11 is guided through corresponding bores to these recesses. 31 indicates the working pressure acting 'on the vane in the direction of arrow C. This pressure is transmitted to the balancing pressure recess 213a through bore 21 as shown in FIG. 7, and like wise to the balancing pressure recess 18a through bore 25. Similarly, balancing pressure recesses 19a and 17a are effected by the pressure medium through the bores 23 and 26. 31 in FIG. 6 shows the Working pressure acting on the vane in the direction of arrow C. 32 and 33 show the pressure acting upon the vane in the balancing pressure fields. As is apparent in FIGS. 6 and in the aforesaid manner, the force of the working pressure acting on the vane is completely balanced by the sumof the orces in opposite direction produced in the individual balancing pressure fields via the recesses.

Where the rotary vane machine is employed in the reverse manner of operation, the pressure at 31 in FIG. 6 acts on the opposite side of the vane and in opposite direction to that of arrow C. Thus, the pressure is not guided to the balancing

pressure recesses

17a, 18a, 19a and Zea, but instead to the balancing pressure recesses l7, l8, l9 and 20 through corresponding bores, and this pressure acts on the sides opposite faces 32 and 33 and in opposite direction.

The larger the outward radial movement of the Vane in the slot, the more will be'the working face of the medium. In FIG. 8, the working medium is effected only in plane 33, since the vane moves slightly radially outwardly within the slot. In this case, as shown in FIG. 4, bores 21 and 25 are still covered by the slot of the rotor, and only recesses 17a and 19a create the balancing pressure fields shown at 32'. In FIG. 9 the vane has traveled further radially outwardly, and bores 21 and 25 in FIG. 4 are positioned externally to the slot of the rotor and abut cell 39 of FIG. 3. In this position, as shown at 34 in FIG. 9, the tangential working pressure acts on vane 11 while the balancing pressure fields created act in the direction indicated by the

pressure arrows

35 and 36.

Although the embodiment shown employs two separate balancing pressure fields at each vane extension, many steps of fields may be used so that the balancing pressure fields and their action increase continuously as the vane travels radially outwardly of the slot. FIG. 10 shows a manner of balancing the radial fluid pressure acting upon the vane bottom. The pressure medium is guided into inner cell 49 beneath the vane and within the slot of the rotor. The pressure medium is also present in cell 45 positioned radially outwardly of the vane within the side walls as shown in FIGS. 8 and 9'. Cell 45 is connected directly with the balancing pressure recesses provided in the slide element. If the area of pressure fields 40 and 37 are the same, the force produced at area 40 will be equal to the force produced at area 37. In this way, the forces in the pressure medium acting radially outwardly upon the vane bottom and inwardly upon the slide element are in balance and the vane, in arrangement with the slide element, freely floats between casing ring '6 and rotor 2. Where field area 37 is greater than area 40, any friction caused by the centrifugal force is offset, under a given pressure in the pump. 44 and 38 show extended surface portions or the sliding member. These portions provide a stable support and a stable sliding of the slide element along casing ring 6, and further, these port-ions perform a sealing action between balancing pressure field 37 in FIG. 10 and the pressure in the working cells of the individual vanes. Rotor 2 has a groove 39 shown in FIG. 10 to fit therein sliding

parts

44, 38, where the vane travels radially inwardly.

Constructions of other embodiments of the slide element of the invention are illustrated in section in FIGS. 11, 12, and 13. The essential characteristic of the slide element in these embodiments is the revolving member which has the same radius as the channel on the top surface of the vane, so that the slide is rotatable around its axis in the channel. The sliding member of the slide element is constructed so that it abuts the side walls of the rotor and slides along the width of the casing ring; the wider sliding part of the slide being adapted to fit closely within a recess in the side wall of the rotor. These balancing pressure fields created in the slide element recesses may result from many recesses or even from one recess.

FIGS. 14, 15 and '16 show a manner of fitting the slide element onto vane 11. Slide member t} rotates with rotating members 51, 52' inserted into the vane, edges 15, 16 of the vane are bent inwardly so that the slide may not become dislodged from the vane. The sliding member of the slide element is closely fitted between the extended side :

portions

15, 16 of the vane 11, sealing the space between sliding member 5% and side edges 15 and 16 of the vane. I

FIGS. 21 and 22 show a constructional form of the slide element consisting of two separate members. Sliding member 64 has a groove 75 into which rotating member 66 can be inserted and secured. FIGS. 23 and 24 show a form of the rotating member. FIGS. 25 and 26 indicate a form of the sliding member. The halved rotating member shown in FIGS. 21-26 has a particular advantage in that it can simply be constructed by grinding a cylindrical pin to form a halved member as shown in FIG. 24. Another advantage is that the rotating memher, as a separate member, can be made so that its length is very accurate. In this way, it can be inserted snugly into the extended side part of the vane shown in FIG. 14. Furthermore, the construction of the slide element in two parts makes it possible to fit the rotating members into the vane, turn in edges 15, 16 (FIG. 15), and later secure the sliding member thereon separately.

The constructional form of the slide members shown in FIGS. 27, 28, 29, 30, 31 and 32 has similar advantages to those of the two-piece slide element shown in FIGS. 21-26. Thus, the rotating member is merely a

shafit

69, 70 in ground cylindrical form, which is simply inserted into groove 72 of sliding member 71. 73 is a balancing pressure recess.

The two-piece slide element shown in FIGS. 27-32, however, can only be employed where the vane and slide are forcibly directed between casing ring 6 and guide rings 56, 57 as shown in FIGS. 17, 18, wherein rotating member 60 of the vane slide element is simply fitted into both grooves of vane 11 and slide member 12. In the embodiment shown in FIGS. 17, 18, it is not necessary to protrude the vane into the side Wall. Consequently, this construction can be applied generally to vanes for conventional pumps. In this case, the pressure medium is directed to the balancing pressure recess 86 from working cell 84 through bore 85 in sliding member 12. Bores are provided radially in vane 11, and compressed springs 61 are disposed in these bores. Each spring is encircled by a spring case, 62, pressing the case radially and inwardly. Spring case 62 has an opened sliding bearing in a semi-cylindrical form enclosing running roller 63'. Roller 63 has a turning groove, into which the hearing of the spring case 62 is fitted. By this fitting, the sliding speed between the spring case 62 and the running roller 63 can be kept at a Passages are turned in the rotor or in the side wall of the rotor tor receiving guide rings '56 and 57. Running roller 63 revolves over guide rings 56, 57. In other embodiments, running roller 63 is divided into two sections. The vane and the slide may be constructed of such accurate dimensions that the spaces between individual parts are so small that sliding roller 60 cannot become dislodged from the slide and vane assembly. Slight tolerances in manufacture are compensated by spring 61 which constantly keeps these parts in tension radially between running

rings

56, 57 and the casing ring.

In FIGS. 19 and 20, another embodiment is illustrated for guiding the vane and slide element forcibly between casing ring 6 and inner running rings 56, 57. A means of keeping the vane and slide assembly forcibly under tension between the casing ring and the guide ring is essential for all vane and slide assemblies having balancing pressure recesses Where no means for preventing the slide element from falling out of the vane are provided.

In the embodiment shown in the FIGS. 19 and 20, sliding

shoes

58 and 59 are inserted into a groove in the bottom face of vane 11 radially and inwardly to the ends of the vane. Sliding

shoes

58, 59 slide on their under side along running

rings

56, 57 as slide element 12 travels along enclosing ring 6. These inner sliding

shoes

58, 59 have as an important feature radial projections provided on the plane thereof which partially encircle guide rings 56, 57, being positioned between guide ring 57 and sidewall 55 or between guide ring 56 and side wall 54. These projections prevent radial movement or axial displacement of the related parts.

FIGURES 33 to 40 FIGURES 41 to 49 and FIGURES 50 to 62, respectively, show various improved embodiments according to the invention in which engagement between the sliding member and the rotating member of the vane slide and engagement between the rotating member and the vane itself permit advantageous employment of bipartite slide members as shown in FIG. 28. These embodiments are simple to manufiacture and provide an improved sealing condition between adjacent vane cells.

In FIGURES 33 to 40, rotating member 79 of the vane slide is simply constructed as a cylindrical rod, more than half the face of which is enclosed :by sliding member 80 of the vane slide upon assembly so that these members cannot be separated. Furthermore, rotating member 79 is pivoted within bore 81 in the extended portion of the vane which slides within the guide slot of the rotor side wall. Consequently, -no leakage can occur between adjacent vane cells caused by lifting rotating member 79 from its channel along the top face of vane 78. The bore 81 of the vane is constructed of a slightly smaller diameter than that of the rotating member 79. Slot 82, disposed between the outer radial end faces of the extended portion of the vane permits rotating member 79 of the vane slide to be slid into bore 81 where it is received under tension.

FIGURES 41 to 49, respectively, show an embodiment similar to those in FIGURES 33 ltO 40, but without provision for a slot. In this embodiment, rotating member 85 of the vane slide is merely pushed and fitted into bore 87 of vane 84. Other features are similar to those of FIGURES 33 to 40.

In the embodiment shown in FIGS. 50 and 52, the halved bearing system, instead of the bore-bearing system, is employed. In this case, rotating member 90 of the vane slide is sustained in the semi-cylindrical shaped groove 92 of vane 89, land is covered by hearing cover 94 from above. Bearing cover 94 is inserted into groove 93 provided at the top face of the extended portion of the vane and is secured to the vane by pin 97 which is inserted through pin holes 95, 96. Rotating member 90 and sliding member 91 of the slide element are similar to those shown in FIGS. 33 to 40 and FIGS. 41 to 49.

FIGURES 63 to 66 show an embodiment of a further means for receiving the vane slide. In this embodiment, a groove 101 is arranged at an angle of about 30 to 45 degrees with respect to the side of the vane, at the extended portion of vane 98. The slide element, consisting of rotating member 99 and the sliding member 100, is inserted into the groove 101 and rotatably supported via both ends of rotating member 99. In its location, within the guide slot of the rotor, the extended portions of the vane are positioned adjacent the side wall of the rotor, and the openings of slot 101 are sealed by the side walls so that the slide element cannot become dislodged during operation.

In the embodiment shown in FIGS. 67 and 68, balancing pressure recess 109 provided on the extended portion of vane 1-0-2 'is open on its bottom side and may be enlarged downwardly toward the lower end of the vane upon radial outward travel of the vane within slot 112. In order to seal the open end of the recess in a downward direction, sealing plate 110, which is adapted to slidably and tightly close recess 109 during the radial inward travel of vane 102, is provided on the side face of the slot 112 of rotor side wall 106 in direct line with recess 109. Plate 110 may be suitably secured, as vfor example, with a pin 111. Thus, during operation of the rotary piston machine, all sides of the pressure recesses creating the counter balancing pressure fields are tightly sealed, allowing entry and exit of the pressure medium only through ducts 113 to similar recesses on the opposite side of the vane. The counter pressure fields created, balance the vane in the slot and permit the vane to float radially inwardly and outwardly during each machine cycle with a minimum of friction, tilting and wear.

In the last mentioned embodiment, during rotation of the rotor, the balancing pressure field created increases and decreases accordingly as the vane moves in and out of the slot, affording a more complete balancing action than the step-like action which takes place where separate recesses are provided in the extended portion of the vane.

It will be obvious to those skilled in the art that while the specification and drawings have been set forth herein to illustrate the invention, various changes and modifications may be made without departing from the spirit and scope of the invention, which is to be limited only by the appended claims.

What is claimed is:

1. A rotary vane type engine comprising a casing having an inner circumferential surface defining -a working chamber for receiving and discharging fluids, a rotor in said working chamber having an axis eccentric with respect thereto and provided with radial slots, vanes substantially radially slidable in said rotor slots and forming with said rotor and with said working chamber, expanding and contracting intervane spaces in which said fluid is received, said rotor extending in said casing axially beyond the axial ends of said Working chamber and said rotor slots in said rotor extending axially beyond the ends of said working chamber, a slide element rockingly mounted longitudinally on each vane for rocking about a longitudinal axis, said slide element having a radially outer side adjacent yet spaced from the casing inner surface and opposed edges extending substantially radially outwardly therefrom in said working chamber to said surface and axially to the ends of said working chamber to maintain sealing contact with said surface and to form therewith and with said radially outer side of said slide element a balance chamber for the reception of pressure fluid, and a passage external to said vanes through the portion of' the rotor slot extending beyond the ends of the working chamber to provide open communication at all times between such balance chambers and the bottom of said rotor slots for the passage of pressure fluid from the bottom of said rotor slots to said balance chambers.

2. Engine according to claim 1 wherein said vanes are axially wider than said intervane spaces and are wholly 12 contained at their ends in said rotor slots, and said balance chambers extend to the axial ends of the vane portions within said working chamber and are axially openended for communication with the bottom of said rotor slots external to said vanes.

3. Engine according to claim 1 wherein said passage is continuously in communication with the pressure side of the rotary vane type engine to receive fluid at the maximum pressure within the casing.

4. Engine according to claim 1 wherein said passage is common to all said rotor slots.

5. Engine according to claim 1 wherein said rotor extends beyond said working chamber laterally and radially at its ends and said vanes also extend laterally beyond said working chamber, said balance chambers at their axial ends communicating with said rotor slots.

6. Engine according to claim 5 wherein the lateral extensions of said vanes slide in corresponding lateral extensions of said rotor slots provided within the portions of the rotor extending beyond said working chamber, said Vane lateral extensions having projections passing radially outwardly of said working chamber and terminating medially at the lateral ends of the slide elements, said passage communicating said balance chamber with the bottom of the corresponding rotor slot extending in part through said projections.

7. Engine according to claim 6 wherein each said projection contains a bore passage extending from the medial end thereof adjacent the corresponding lateral end of the slide element to the distal end thereof in communication with an end portion of the rotor slot:

8. Engine according to claim 1 wherein spring tension means are positioned at each end of each said vane, and radially inwardly of the vane in the rotor slot, and roller means are positioned radially inwardly of said spring means, said spring means being seated partially within a recess in the under side of said vane at the radially outward side of said spring means and abutting a revolving goove in said roller means at the radially inward side of said spring means, whereby said spring means during operation of the engine are capable of keeping said roller means and said slide element in slight compression against their respective abutting parts.

9. Engine according to claim 1 wherein sliding shoe means are positioned at each end of each said vane and radially inwardly of the vane in the rotor slot, and guide ring means are positioned partially medially and radially inwardly of said sliding shoe means, said shoe means being seated partially along a recess in the under side of said vane at the radially outward side of said shoe means and seated laterally and downwardly about said guide ring means at the radially inward side of said shoe means, whereby said shoe means during operation of the engine are capable of keeping said guide ring means radially inwardly thereof and said slide element on said vane radially outwardly thereof in slight compression against their respective abutting parts.

l0. Vane assembly, for a rotary vane type engine, which comprises a longitudinally extending vane having a top face and a bottom face, a vane lateral extension being provided at each longitudinal end of the vane, each vane lateral extension having a projection passing upwardly beyond the top face of said vane, said top face being provided with a longitudinally extending groove therein and each said projection being provided with a corresponding bore passage, a rocker rod extending along said groove in said top face and being pivotally secured at its ends within said bore passages, and a slide element disposed on said rocker rod and extending along said top face for pivoting with said rod.

11. Engine according to claim 10' wherein said rocker rod and slide element are integral.

12. Engine according to claim l O wherein said rocker rod has a substantially flat top surface and a curved bottom surface, said slide element being secured to said rocker rod along a portion of said flat top surface, said flat top surface being received within a corresponding substantially fiat groove located within the bottom surface of said slide element.

13. Engine according to claim wherein said rocker rod has a substantially curved top surface and a bottom surface, said slide element being secured to said rocker rod along a portion of said curved top surface, said curved top surface being received within a corresponding substantially curved groove located within the bottom surface of said slide element.

-14. Engine according to claim 10 wherein said bore passage communicates with one face of the corresponding projection of the vane extension along its length by means defining a slot, whereby said rocker rod may be positioned within said bore passage through said slot.

15. Engine according to claim 14 wherein said slot is an inclined slot defined in a side face of said projection of the vane extension passing downwardly to said bore passage.

16. Engine according to claim 14 wherein said bore passage is of slightly smaller diameter than that of said rocker rod and said slot is of slightly narrower width than the diameter of said bore passage, whereby said rocker rod may be positioned within said bore passage under slight tension.

17. Engine according to claim 10 wherein each projection has a top face upwardly beyond the vane top face, and said bore passage is defined by a groove extension positioned within the bottom portion of a channel defined in the top face of the projection of the vane extension, said groove extension communicating with the groove along the top face of said vane, in conjunction with removable means defining a complementary top groove positioned within said channel over said groove extension.

18. Engine according to claim 17 wherein additional means including pin means are provided for securing said means defining a complementary top groove within said channel.

19. In a vane assembly, for rotary fluid machine of the type having a casing with an inner circumferential surface defining a working chamber and a rotor with slots for carrying slidable vanes in slidable sealing contact with the casing inner surface to form intervane spaces in the working chamber, the improvement which comprises a longitudinally extending vane having a central portion and two end portions, said end portions extending transversely beyond said central portion, a slide element disposed between said end portions of said vane, for cooperation with the inner circumferential surface of the casing to form a seal, and support means extending into said end portions for supporting said slide element between said two end portions.

i20. In a vane assembly, for rotary fluid machines of the type having a casing with an inner circumferential surface defining a working chamber and a rotor with slots for carrying slidable vanes in slidable sealing contact with the casing inner surface to form intervane spaces in the working chamber, the improvement which comprises a longitudinally extending vane having a central portion with a top face which is smaller in height than the two end portions of the vane, said end portions each having a transverse medial face adjacent said top face, sliding means pivotal between said end portions for cooperating with the inner circumferential surface of the casing to form a sliding seal, said sliding means having transverse end faces abutting the medial faces of said end portions and cooperating therewith to form a seal therebetween, the medial faces of said end portions extending upwardly beyond the uppermost portion of the corresponding sliding means transverse end face.

21. Improvement according to claim 20 wherein means are included extending into said end portions for pivotally supporting said sliding means between said end portions.

22. Improvement according to claim 21 wherein said sliding means is wider than said vane, and wherein pivotal means are included which are carried on a retaining seat on the central portion of said vane for pivotally supporting said sliding means.

References Cited in the file of this patent UNITED STATES PATENTS 1,658,524 Gurley Feb. 7, 1928 2,149,337 Deming Mar. 7, 1939 2,545,238 MacMillin et a1 Mar. 13, 1951 2,658,456 Wahlmark Nov. 10, 1953 2,746,392 Klessig et a1 May 22, 1956 2,755,741 Erskine July 24, 1956 FOREIGN PATENTS 9,499 Great Britain Of 1915 139,293 Austria Nov. 10, 1934 568,518 Great Britain Apr. 9, 1945 606,413 Great Britain Aug. 12, 1948

Claims

1. A ROTARY VANE TYPE ENGINE COMPRISING A CASING HAVING AN INNER CIRCUMFERENTIAL SURFACE DEFINING A WORKING CHAMBER FOR RECEIVING AND DISCHARGING FLUIDS, A ROTOR IN SAID WORKING CHAMBER HAVING AN AXIS ECCENTRIC WITH RESPECT THERETO AND PROVIDED WITH RADIAL SLOTS, VANES SUBSTANTIALLY RADIALLY SLIDABLE IN SAID ROTOR SLOTS AND FORMING WITH SAID ROTOR AND WITH SAID WORKING CHAMBER, EXPANDING AND CONTRACTING INTERVANE SPACES IN WHICH SAID FLUID IS RECEIVED, SAID ROTOR EXTENDING IN SAID CASING AXIALLY BEYOND THE AXIAL ENDS OF SAID WORKING CHAMBER AND SAID ROTOR SLOTS IN SAID ROTOR EXTENDING AXIALLY BEYOND THE ENDS OF SAID WORKING CHAMBER, A SLIDE ELEMENT ROCKINGLY MOUNTED LONGITUDINALLY ON EACH VANE FOR ROCKING ABOUT A LONGITUDINAL AXIS, SAID SLIDE ELEMENT HAVING A RADIALLY OUTER SIDE ADJACENT YET SPACED FROM THE CASING INNER SURFACE