GB2192939A

GB2192939A - Sliding vane pump

Info

Publication number: GB2192939A
Application number: GB08717229A
Authority: GB
Inventors: Hiroshi Sakamaki; Yukio Horikoshi; Takeshi Jinnouchi; Kenji Tanzawa
Original assignee: Eagle Industry Co Ltd
Current assignee: Eagle Industry Co Ltd
Priority date: 1986-07-22
Filing date: 1987-07-21
Publication date: 1988-01-27
Anticipated expiration: 2007-07-21
Also published as: GB2192939B; GB8717229D0; IT1211222B; KR920007283B1; DE3724128A1; IT8767627A0; KR880001927A

Description

GB2192939A 1

SPECIFICATION Type;

Fig. 20 is a'side view of a rotor of the Vane pump same pump; Fig. 21 is an explanatory view showing the The present invention relates to pumps and in 70 operating state of the vane pumps shown in particular to rotary pumps such as are used in Figs. 1 to 3; r the supercharger of the engine or a compres- Fig. 22 is an exploded perspective view of sor of a freezing system. essential parts of a vane pump belonging to According to the present invention there is Type 4; provided a vane pump which is characterised 75 Fig. 23 is a side view of a rotor of the in that projections such as pins are provided same pump; on both ends of a vane, and an annular race Fig. 24 is an explanatory view comparing in peripheral slidable engagement with said the mounting state of the vane of the same projections to define an appearance of the pump with Fig. 21; vane from a vane groove is formed coaxially 80 Fig. 25 is a'sectional view of a vane pump with the inner peripheral surface of the hous- belonging to Type 5; ing. Fig. 26 is &sectional view of a vane pump According to the present invention, the belonging to Type 6; appearance of the vane from the vane groove Fig. 27 is a'side view of a rotor of the is not defined by the contact thereof with the 85 same pump; inner peripheral surface of the housing but it is Fig. 28(1) and 28(11) are respectively perspec defined in a manner such that the end edge of tive views of etainer rings; the vane depicts a certain locus by the en- Fig. 29 is a'sectional view of the vane gagement of the projections such as pins pro- pump belongifig to the. same Type; vided on the vane with the annular race 90 Fig. 30 is dsectional view of a vane pump formed on the side of the housing. The vane belonging to Type 7; may be rotated in the state in which the vane Figs. 31, 32 and 33 are respectively per is not in contact with the inner surface of the spective views of retainer rings; housing, and therefore, the present invention Fig. 34 is an exploded perspective view of has excellent advantages which can prevent 95 a vane pump belonging to Type 8; the deterioration of the efficiency of pump Fig. 35 is a sectional view showing the as caused by the sliding resistance and the wear sembling state of the same pump; of the vane; and which can prevent an occur- Fig. 36 is a side view of a rotor of the rence of inconveniences resulting from an in- same pump; crease in sliding heat. 100 Fig. 37 is dside view of a rotor of the Vane pumps embodying the present inven- pump belonging to the same Type; and tion will now be described, by way of Fig. 38 is asectional view showing one example, with reference to the accompanying example of a previously proposed vane pump.

diagrammatic drawings, in which: The previously proposed vane pump shown Fig. 1 is an exploded perspective view of a 105 in Fig. 38, includes a housing 101, a rotor vane pump according to a fundamental em- 102 inserted eccentrically into an inner periph bodiment of the present invention, eral space of the housing 101 and rotatably Fig. 2 is a sectional view showing an as- supported by b rotational shaft 103, three sembling state of the same vane pump, plate-like vanes 105a, 105b and 105c are dis Fig. 3 is a side view of a rotor of the same 110 posed radiaIlyretractably in respective vane pump; grooves 104a, 104b and 104c equally spaced Figs. 4, 5, 6 and 7 are perspective views of apart so as to peripherally divide the outer vanes, respectively; peripheral side of the rotor 102 into three Fig. 8 is a perspective view, partly cutaway, sections. Whn the rotor 102 is rotated in the of a vane of the pump belonging to Type 1; 115 direction as indicated by the arrow X by the Figs. 9, 10, 11, 12, 13 and 14 are respec- rotational shaft 103, the vanes 105a, 105b tively perspective views of essential parts and 105c are'moved out in the direction of showing the internal construction of the vane the outside diameter by the centrifugal force, belonging to the same Type; and the end edges thereof rotate while sli- Fig. 15 is a perspective view, partly cu- 120 dably contacting the inner peripheral surface of taway, of a vane of a pump belonging to the housing 101. Since the rotor 102 is ec Type 2; centric with respect to the housing 101 as Fig. 16 is a perspective view of the vane of previously mentioned, as such rotation occurs, the pump belonging to the same Type; volumes of working spaces 106a, 106b and Fig. 17 is a perspective view of essential 125 106c defined 'by the housing 101, the rotor parts of a vane pump belonging to Type 3; 102 and the Vanes 105a, 105b and 105c are Fig. 18 is a side view of the vane of the repeatedly enf ' arged and contracted to allow a same pump; fluid taken in from an intake port 107 to be Fig. 19 is an exploded perspective view of discharged out of an outlet port 108.

the vane of the pump belonging to the same 130 However, the abovedescribed conventional 2 GB2192939A 2 vane pump has problems that since the vanes edges 11 a', 11 b' end 11 c' (see Fig. 3) thereof slidably move along the inner peripheral sur- and the inner peripheral surface 'I" of the front face of the housing at high speeds, the effici- housing 1. An intake port 19 for guiding a ency of volume caused by the great power fluid into the inner peripheral space 5 of the loss due to the sliding resistance and by the 70 housing from the exterior of the pump and an generation of high sliding heat unavoidably de- outlet port 20 for guiding a fluid to the exte teriorates; the vanes materially become worn; rior from the inner peripheral space 5 of the and the vanes are expanded due to the gener- housing are formed in the rear housing 2. Ref ation of sliding heat to produce a galling with erence numerals 21, 21 designate tubes the inner side surfaces of both end walls of 75 mounted on the intake port 19 and outlet port the housing, and the like. 20, respectively; 22 a bolt used to secure the A fundamental embodiment of a vane pump bearing cover 8 to the rear housing 2; and embodying the present invention will now be 23, a nut in engagement with an external described with reference to Figs. 1 to 3. thread 10' of the end of the rotational shaft In Figs. 1 and 2, a front housing 1 and a 80 10 in order to secure the pulley 9 to the rear housing 2, which both housings are made rotational shaft 10.

of non-ferrous metal such as aluminium which The operation of the abovedescribed vane is light in weight and is small in the coefficient pump will bedescribed hereinafter. When the of thermal expansion, are secured integral with rotational shaft 10 and rotor 4 are rotated by each other by means of bolts 3. A rotor 4 85 the drive force from the pulley 9, the vanes made of iron eccentrically inserted into an in- 11 a, 11 b and' 11 c also rotate, and the pins ner peripheral space 5 of the housing is ex- 13 and 13 projected on the vanes 11 a, 11 b tended through both the housings 1 and 2 and 1 lc, respectively, and the sleeve bearings through a ball bearing 7a held by a fixed ring 14 and 14 slipped over the pins 13 and 13 6 in anti-slipout fashion in an axial fixed ring 6 90 rotate along the annular races 17 and 17, in anti-slipout fashion in an axial shoulder of Since as shovn in Fig. 3, the inner peripheral the front housing 1 and a ball bearing 7b held surface 'I" of the housing and the annular race by a bearing cover 8 in anti-slipout fashion in 17 are in the ' coaxial relation and the annular an axial shoulder of the rear housing 2 and is race 17 and the rotor 4 are in the eccentric rotatably mounted on a rotational shaft 10 to 95 relation, the vanes 11 a, 11 b and 11 c are radi which adrive force is transmitted from a pulley ally slidably moved in the vane grooves 12a, 9. Plate-like vanes 11 a, 11 b and 11 c princi- 12b and 12c!of the rotor 4 to be projected pally made of a carbon material having an ex- and retracted repeatedly with the result that cellent slidability are disposed to be radially the volumes of the working spaces 5a, 5b projected and retracted in vane grooves 12a, 100 and 5c defined by both the housings 1, 2, the 12b and 12c, respectively, which are formed rotor 4 and the vanes 11 a, 11 b and 11 c re in the form of a depression in equally spaced peatedly incre'ase and decrease. That is, in apart so as to peripherally divide the outer Fig. 3, the working space 5a, with the rota peripheral side of the rotor 4 into three sec- tion, increases its volume to suck the fluid tions, on the rotor 4. On opposite ends of 105 from the intake port 19 (not shown; see Fig.

each of the vanes 11 a, 11 b and 11 c corre- 1) opening to: said portion; the working space sponding to axial opposite sides of the rotor 5c, with the r ' otation, decreases its volume to 4 are projected steel pins 13 and 13, re- discharge the,fluid into the outlet port 20 (not spectvely, and a sleeve bearing 14 made of shown; see F!g. 1) opening to said portion; resin having excellent slidability and abrasion 110 and the working space 5b transfers the thus resistance is slipped over each of said pins sucked fluid tbward the outlet port 20. In the 13. In annular recesses 15a and 15b formed above-descriUed operation, the end edges in inner surfaces 1' and 2' of end walls where lla', 11W and llc' of the vanes 11a, 11b the front housing 1 and the rear housing 2 are and 1 '1 c are not in the sliding contact with the opposed to each other coaxial with the inner 115 inner peripheral surface 'I" of the front hous peripheral space 5 of the housing (coaxial with ing, as previously mentioned, and therefore, an inner peripheral surface V' of the front abrasion or high heat hardly occurs. In addi housing 1), retainer rings 16a and 16b made tion, the slee'e bearing 14 slipped over the v of non-ferrous metal such as aluminium and pin 13 is sliddbly rotated while being pressed each having an annular race 17 are rotatably 120 against the outside diameter side by the cen fitted through ball bearings 18a and 18b, re- trifugal force Within the annular race 17 of the spectively. The pins 13 and 13 projected on retainer rings 16a and 16b while the retainer the respective vanes 11 a, 11 b and 11 c per- rings 16a and 16b follow the sleeve bearing ipherally slidably engage the annular races 17 14 for rotation because the former are in the and 17 of the retainer rings 16a and 16b 125 state to be rotatable by the ball bearings 18a through the respective sleeve bearings 14. and 18b, respectively. The relative sliding This engagement defines the radial movement speed between the sleeve bearing 14 and the of the vanes 11 a, 11 b and 11 c during rota- annular race 17 is low whereby the abrasions tion so as to maintain a state in which there of these annular race 17, retainer rings 16a is formed a slight clearance between the end 130and 16b, the sleeve bearing 14 and the like 3 GB2192939A 3 can be minimised. great. In addition, since the metal plate has It is believed that the fundamental mode of the punched portions thus considerably reduc the present invention is now fully understood ing the weight, and the nonlubricated sliding from the abovedescribed description. The materials on both sides of the metal plate are pump of the first embodiment shown in Figs. 70 fused to each other through the punched por 1 to 3 constitutes, in a sense, the core of the tions, and therefore the strength of the vane variation described below. body itself also increases.

Fig. 4 shows the mode different from the One example of the vane belonging to the above-described first embodiment with respect type 1 will be described below with reference to the technique in which projections are pro- 75 to the drawings.

vided on the vane. Referring first to Fig. 8, reference numeral That is, in Fig. 4, cylindrical pins 13 made 11 designates a plate-like vane body coated of iron or non-ferrous metal are embedded at with a non-lubricated sliding material 26 hav positions one-sided on parts which form the ing excellent self- lubricating properties such as inside diameter side in the state incorporated 80 resins, mould carbon, etc. using a metal plate into the rotor 4 of opposite ends 11 " and 11 27 made of steel or non- ferrous metal such of a plate-like vane 11 which is made of car- as aluminium having a plurality of circular bon or the like and in which end edges 11' punched portions 28 as a core, and reference which form the outside diameter side in the numeral 13 designates pins which are projec state incorporated into the rotor 4 are formed 85 tions projected from opposite ends of the into R. Alternatively, as shown in Fig. 5, a vane body 11. A base 13a of the pin 13 is lengthy pin 13 is extended through and secaulked to one long side 27a of the metal cured to the vane 11, and opposite ends of plate 27 and is made integral with the metal the pin 13 are projected; as shown in Fig. 6, plate 27 by applying spot welding at 29 to pins 13 and 13 are embedded into the vane 90 suitable points of the caulked portion.

11 and integrally provided by welind or the Modes of the fixed portion between the pin like on opposite ends of a plate-like reinforc- 13 and the metal plate 27 include an arrange ing member 24 made of iron or non-ferrous ment as shown in Fig. 9 in which a base (not metal such as aluminium; or as shown in Fig. shown) of a pin 13 is joined to a groove 30 7, pins 13 and 13 are housed into tubular 95 formed in the vicinity of one long side 27a of bodies 25 and 25 formed on opposite ends the metal plate 27, and the base and the of a reinforcing member 24. groove 30 are joined by spot welding at 29 Several modes of embodiments of the pre- at suitable points; an arrangement as shown sent invention variously elaborated on the ba- in Fig. 10 in which a base 13a of a pin 13 is sis of the design of the pump according to 100 joined to a trough portion 31 formed integral the aforementioned first embodiment shown in with one long side 27a of a metal plate 27, Figs. 1 to 3 will be discussed below. and the base 13a and the trough portion 31 are joined by spot welding at 29 at suitable Type 1 points; an arrangement as shown in Fig. 11 in A vane pump belonging to the type 1 is 105 which a punched portion 28 of a metal plate characterised by having a vane wherein a vane 27 is formed into a square, and one long side body is coated with a non-lubricated sliding 27a of the metal plate 27 and a base 13a of material using a metal plate having a required a pin 13 are applied with spot welding at 29 number of punched portions as a core, and from one edge 28a of the punched portion projections are integrally secured to or inte- 110 28; and an arrangement as shown in Fig. 12 grally formed on the metal plate. in which one long side 27a is interiorly formed In the vane pump according to the aforewith a pin receiving hole 32 from both ends mentioned first embodiment, a great outward 27h of a metal plate 27, and a pin 13 is force caused by a centrifugal force exerts on hammered into said hole.

the pin which is a projection to define the 115 In addition, the pin 13 and the metal plate appearance of the vane and the fixed portion 27 may be integrally moulded by moulding between the pin and the vane, and therefore means such as casting or forging as shown in the strength of said portion and the reduction Figs. 13 and 14. The shape of the punched in weight of the vane need be taken into con- portion 28 has various modifications such as sideration. 120 circular shapes as in Figs. 8 to 10 and 12, a For this reason, an object of the aforesaid ' square shape as in Fig. 11, a cutout shape as type 1 is to enhance the strength between the in Fig. 13, and a triangular shape as in Fig.

vane and the projection and reduce the weight 14. Other shapes such as an oblong shape, a of the vane. shape with a large number of pores, etc. may In the vane of the pump belonging to this 125 be used.

type 1, the projection is integral with the As described above, according to the vane metal plate as the reinforcing core, and the for the pump described above, the supporting base of the projection on the side of the force against the appearance of the vane dur metal plate is coated with the non-lubricated ing rotation by the projections on the opposite sliding material, and therefore the strength is 130 ends of the vane is strengthened, and there- 4 GB2192939A 4 1 fore the high-speed rotation becomes possible provided in the vicinity of the base 11---in to enhance the feed force of the fluid under place of the cutout 3$ shown in Fig. 15 to pressure. Accordingly, the pump may be mini- form a cavity 34, and other structures of Fig.

aturised and reduced in weight. Furthermore, 16 are similar to those shown in Fig. 15.

the metal plate serving as the core of the 70 In the Figs. 15 and 16 structure, the local vane has the punched holes to suppress the stress concenration is hard to occur between increase in weight of the vane and the in- the vane 11 w hich tends to be moved out by crease in the centrifugal force acting on the the centrifugal' force during rotation and the vane. Moreover, the non-lubricated sliding ma- pin 13 to define it, as previously mentioned.

terials coated on the both sides of the metal 75 Since each of the mounting holes 36 is short, plate become fused to each other through the their working May be carried out easily and punched portions, and therefore the strength with high accuracy, and the weight of the of the vane body itself also increases, thus vane 11 is reduced through the portion of the providing a significant practical effect. cavity 34.

80 It is to be noted that the cavity 34 is sub Type 2 sequently fille with resins or the like whereby A vane pump belonging to this type 2 has a the fixing streigth between the vane 11 and vane for a pump characterised in that a cavity the pin 13 may be further increased.

such as a cutout is formed in the base of the As described above, according to the vane, mounting holes are made coaxially to 85 above-described vane, the fixing strength be each other in sleeves which are located on tween the projections (pins) provided on the opposite sides of the cavity in a longitudinal opposite ends of the vane and the vane is direction, and projections of a single pin are high to increase the supporting force against inserted into the mounting holes, respectively. the appearance of the vane during rotation, An object of the type 2 is, likewise the type 90 and therefore, the high speed rotation be 1, to enhance the projections and the fixed comes possible to enhance the feed force of portion between the projections and the vane. the fluid undet pressure. Accordingly, the In the vane of the pump belonging to the pump may beminiaturised and reduced in type 2, the projections on the opposite ends weight. Moreover, the mounting holes through of the vane are in the form of a single rod, 95 which pins exiend-are divided by the cavity and therefore, there is no local stress concen- and shortened, and therefore drilling of the trated on the fixed portion relative to the vane mounting holes may be carried out easily and (the fitted portion to the mounting hole), and with high accuracy, thus providing a great the supporting force against the appearance of practical effect.

the vane is enhanced. In addition, since the 100 mounting holes through which the pin extends Type 3 are divided by the cavity, drilling process may A vane pump belonging to this type 3 has a be executed with high accuracy as compared vane for a purrip characterised in that a vane to the case in which a single mounting hole body and the.aforesaid projections are formed passing through and between the opposite 105 integral with each other of the same material.

ends of the vane is bored, and in addition, the An object of the type 3 is to enhance the weight of the vane is reduced through a por- strength between the vane and the projections tion of the cavity. and reduce the weight of the vane, similarly to One example of the vane belonging to the the types 1 and 2.

type 2 will be described below with reference 110 According to the vane for the pump belong to the drawings. ing to the type 3, no local residual stress or First, in Fig. 15, a vane indicated at 11 is stress concenration between the vane body formed of a non-lubricated sliding material and the projections as encountered in the such as resin or mould carbon having excel- case in which,the vane body and the projec lent self lubricating properties, and a cutout 115 tions are formed from separate members, and 33 is made in the central portion of the base they are joined together by fitting or the like, 11---of the vane 11 to form a cavity 34. and the weight of the vane is small as com Mounting holes 36 are coaxially bored in pared to the 6ase in which the projections are sleeves 35 and 35, respectively, on opposite formed from 'Metal rods fitted into the vane sides in a longitudinal direction of the cutout 120 body. 1 33. Reference numeral 13 designates a single One exampl'e of the vane belonging to the rod-like pin inserted into and secured in the type 3 will now be described with reference mounting holes 36 and 36, and opposite ends to the drawin4s.

of the pin 13 projecting from the sleeves 35 First in Fig. 17, vanes indicated at 11 are and 35 constitute projections, which peripherdisposed to be radially projected from and re ally slidably engage the annular race (see the tracted into vane grooves 12, respectively, number 17 of Figs. 1 and 2) on the side of which are equally divided into three sections the pump housing to define the appearance of in a rotor 4 rotatably supported, in eccentric the vane 11 during rotation. fashion, within a housing not shown, the Next, in Fig. 16, a window portion 37 is 130vanes being formed of an iron sheet, light- GB2192939A 5 1 weight non-ferrous metal such as aluminium, tact area is lage so that the annular race 17 resins or the like, and prismatic projections 38 (the retainer ring 16) may be allowed to be are projectingly moulded integral with opposite smoothly rotated along therewith at the start.

ends in a longitudinal direction of the vane Moreover, since the pressing force per unit body taking the form of a plate. Sliding mem- 70 area in the contact surface lowers, mutual bers indicated at 39 each having an approxi- abrasion is also suppressed.

mately cylindrical contour are externally fitted As described above, according to the at cutouts 40 have a shaped section in the above-described vane for the pump, the vane projection 38, respectively, the sliding mem- body and the projections to define the appear bers being formed of resins having excellent 75 ance of the vane caused by the centrifugal self-lubricating properties and abrasion resis- force by engagement with the annular race tance. A retainer ring indicated at 16 is rotata- rotatably provided on the side of the housing bly mounted through a ball bearing not shown to thereby enhance the supporting force of on each of inner surfaces of the housing op- the projections with respect to the vane body posed to each of the end surfaces of the ro- 80 and reduce the weight of the vane. Thereby, tor 4 in the state in which the retainer is the pump may be run at high speeds, thus coaxial with the inner peripheral surface of the providing the excellent effects of realisation of housing, in other words, it is eccentric at A the miniaturisation and reduction in weight of with the rotor 4. The sliding members 39 ex- the pump.

ternally fitted on the projections 38 of the 85 vanes 11, respectively, peripherally slidably Type 4 engage the snnular recess 17 formed in the A vane pump belonging to this type 4 is opposed end of the retainer rings 16, characterised in that projections are one-sided whereby the appearance of the vanes 11 from toward the inner peripheral surface of the the vane grooves 12 caused by the centrifugal 90 housing rather than the lengthwise central por force during rotation are defined, and the tion between the opposite ends of the vane vanes 11 are radially projected and retracted to form an annular race to have a larger dia and rotated in the state of non-contact with meter accordingly.

the inner peripheral surface of the housing. Also in the vane pump shown in Figs. 1 to According to the above-described arrange- 95 3, in the case where the supporting of the ment, since the vane body of the vane 11 is vane 11 caused by the engagement between moulded integral with the projections 38, the the projections 13 and the annular race 17 as local stress concentration caused by the load shown therein is effected on the inside dia during rotation is hard to occur, and the meter side, the axial oscillation is derived to weight of the vane is small. Therefore, the 100 the vane 11 by repeated changes in pressure projections 38 can sufficiently support the in the periphery of the vane 11 with pumping, vane body even during the rotation at high to fail to perform radial parallel movement speeds. As the vanes 11 rotate, the sliding and when the vane 11 is tilted, it comes into members 39 smoothly slidably move along contact with the housing 1 to produce an ab the peripheral wall 17' (shown in Fig. 18) on 105 normal noise and produce galling with an the outer peripheral side of the annular race opening or the like internally of the intake port 17 but the amount of slidable movement 19. In addition, such contact between the thereof is small because the annular race 17 vane 11 and the housing 1 entails inconve (the retainer ring 16) is also synchronously ro- niences such as the rise in temperature, the tated by the sliding contact therebetween. 110 lowering of the volume efficiency, the pro Next, the Fig. 19 arrangement is character- gress of abrasion etc, caused thereby.

ised in that projections 38 provided on oppo- In the light of the foregoing, the vane pump site ends in a longitudinal direction of a vane belonging to the type 4 is intended to sup body are formed into a cylindrical configura- press the oscillation of the vane during rotation, and sliding members 39 are formed into 115 tion to thereby prevent an occurrence of a somewhat elongated configuration having noises and to further enhance the pump per arched surfaces 39a and 39a; since an angle formance.

of the vane 11 to the annular race 17 is re- For achieving the aforesaid object, the vane peatedly varied within a predetermined range pump of the type as described has a rotor with rotation as shown in Fig. 20, the sliding 120 rotatably supported in eccentric fashion within members 39 are slipped over the projections an inner peripheral space of a housing and 38 at circular holes 41 bored in the sliding vanes each disposed to be projected from and members 39, respectively, to thereby enable retracted in each of a plurality of vane the relative oscillation with respect to the grooves formed in the rotor, wherein projec vane 11. 125 tions formed on opposite ends of each of the According to the aforesaid arrangement, the vanes are brought into peripherally slidable en arched surface 39a of the sliding member 39 gagement with annular races provided coaxi comes into contact with the peripheral wall ally and rotatably in the inner peripheral sur 17' of the annular race 17 by virtue of the face of the housing internally of the housing, centrifugal force during rotation, and said con- 130 and wherein the projections are to be posi- 6 GB2192939A 6 tioned one-sided toward the inner peripheral characterised in that a retainer ring coaxial surface of the housing rather than the length- with an inner peripheral space of a housing is wise central portion between the opposite fitted through a bearing internally of the end ends of the vane to form the annular races to wall of the housing, and the retainer rings are have a larger diameter correspondingly. That 70 engaged with the aforesaid vanes to define is, since the supporting of the vanes against the appearance of the vanes from the vane the appearance thereof is effected on the side grooves, and a backup ring to suppress the of the outside diameter, the axial oscillation of oscillation of the retainer rings is interposed the outside diameter portion of the vane between the retainer ring and the end wall of around the projections may be suppressed to 75 the housing.

prevent it from coming into contact with the Since in the vane pumpbelonging to the housing. type 5, the backup ring is interposed between One example of the vane pump belonging to the retainer ring and the end wall of the hous the type 4 as described will now be described ing to suppress the oscillation of the retainer with reference to the drawings. 80 ring caused by the oscillation of the bearing in In Figs. 22 to 24, projections 38 are formed the thrust direction, the retainer ring may be on opposite ends 11" of a vane 11 in an axial smoothly rotated and the vane may be direction of a purnp,. the projections being po- smoothly projected and retracted.

sitioned to be one-sided toward the inner per- One example of the vane pump belonging to ipheral surface of the housing 1 rather than 85 the type 5 will be described hereinafter with the lengthwise central portion between the respect to the drawings.

opposite ends 11", in other words, toward ' As has been described so far and as again the outside diameter side. Retainer rings indi- shown in Fig. 25, a clearance between mem cated at 16 are rotatably mounted through ball bers such as the rotor 4, retainer rings 16a, bearings 18 on both inner surfaces of the 90 1 6b and vanes 11 a, 11 b, 11 c to be projected housing 1 and 2 in a manner coaxial with said and retracted with the rotation is set to be housings 1 and 2, that is, in the state eccen- extremely small in view of the improvement in tric with respect to the rotor 4 through a di- the pump efficiency. In addition, the vanes mension indicated at A. An annular race 17 11 a, 11 b and 11 c are supported on the re adapted to peripherally slidably engage the 95 tainer rings 16a and 16b by the engagement projection 38 of the vane is recessed in the between the pins 13 and the annular races end opposed to a flange 16' of each of the 17, respectively, and the retainer rings 16a retainer rings 16, the annular race 17 being and 16b themselves need be firmly supported formed to have a large diameter correspond- so as not to cause oscillations of the retainer ing to the projected position of the projection 100 rings 16a and 16b and smoothly rotated in 38. order that the vanes 11 a, 11 b and 11 c may According to the above-described arrange- be smoothly projected and retracted. How ment, the axial oscillation of the portion on ever, practically, the retainer rings 16a and the outside diameter side from the projection 16b are axially oscillated by the oscillations of 38 of the vane (the portion above the phan- 105 the ball bearings 18a and 18b in the thrust tom line in Fig. 24), around the projection 38, direction and by the distribution of pressure is suppressed, and the opposite ends 11" of within the working space 5, resulting in the the vane in the axial direction of the pump are contact thereof with the end walls of the guided by the flanges 16' of the retainer rings housings 1 and 2, as a consequence of which 16, respectively, and therefore the contact 110 the vanes 11 a, 11 b and 11 c tend to be devi thereof with the housings 1 and 2 will not ated or inclined. In the pump as herein pro occur. posed, taking this into consideration before As described above, according to the afore- hand, backup rings 42a and 42b are inter mentioned vane pump, the projections in en- posed between the retainer rings 16a and 16b gagement with the annular races are provided 115 and the housings 1 and 2 to prevent the os one-sided toward the outside diameter side cillations of the retainer rings 16a and 16b.

rather than the lengthwise central portion of The backup rings 42a and 42b formed of car the opposite ends of the vane in the radial bon or non-lubricated sliding material such as direction of the pump to thereby suppress the resins are fitted ' in annular grooves 43a and axial oscillation of the vane during operation to 120 43b positioned in parts of the annular re prevent the contact thereof with the housings. cesses 15a and 15b formed in the end walls The occurrence of abnormal noises, abnormal of the housings 1 and 2, the ends of which abrasion, and deterioration of volume effici- are placed in abutment with the backs of the ency resulting from said contact have been retainer rings 16a and 16b. The backup rings overcome, thus exhibiting an excellent per- 125 are strengthened in supporting force by em formance for use with a supercharger, a com- ployment of a number of coil springs 44 as pressor and the like for automobiles. necessary to prevent oscillations of the re tainer rings 16a and 16b so that the retainer Type 5 rings 16a and 16b may not contact with the A vane pump belonging to this type 5 is 130 end walls of the housings to indirectly secure 7 GB2192939A 7 the smooth operation of the vanes 11 a, 11 b are defined in their radial movement and can and 11 c. rotate in non-contact with the inner peripheral According to the vane pump as described surface of the housing. Small- diameter bosses above, the backup rings are provided on the indicated at 48a and 48b are provided to im backs of the retainer rings to suppress the 70 pede unnecessary retraction of the vanes 11 a, oscillations of the retainer rings to stabilise 11 b and 11 c into the vane grooves 12a, 12b the rotation of the retainer rings. Therefore it and 12c when the pump stops, and to avoid becomes possible to smoothly project and re- an excessive shock between the pins 13 and tract the vanes, thus preventing harmful influ- 13 and the journal bearings 45a and 45b ences resulting therefrom. 75 caused by the sudden appearance of the vanes 11 a, 11 b and 11 c when the pump Type 6 starts, the bosses being projected concentric A vane pump belonging to this type 6 is with the annular recesses 15a and 15b.

characterised in that bearings are rotatably This vane pump is constructed as described mounted coaxially with the inner peripheral 80 above. When the rotational shaft 10 and the surface of a housing internally of both end rotor 4 are rotated in the direction as indi walls of the housing, and projections provided cated at X by the drive force from the pulley on both side ends of vanes opposed to said 9, the vanes 11 a, 11 b and 11 c rotate in non end walls and the inner peripheral surfaces of contact with the front housing 1 and the rear the bearings are brought into contact with 85 housing 2 with the pins 13 and 13 placed in each other to define the appearance of the contact with the inner peripheral surfaces of vanes during rotation. the journal bearings 45a and 45b by virtue of That is, the vane pump belonging to the the centrifugal force.

type 6 is designed to use bearings in place of In the above-described operation, the vanes the retainer rings used in the vane pumps as 90 11 a, 11 b and 11 c are totally free from sliding previously described to save trouble of form- contact with the front housing 1 and rear ing annular races in the retainer rings. Accord- housing 2 as previously mentioned while the ing to this arrangement, in the vane moved pins 13 and 13 integral with the vanes 1 '1 a, out of the vane groove by virtue of the centri- 11 b and 11 c comes into sliding contact with fugal force during rotation, the projections on 95 the journal bearings 45a and 45b but the the opposite ends thereof come into contact amount of sliding contact thereof is small be with the inner peripheral surfaces of the bear- cause the journal bearings 45a and 45b rotate ings provided coaxially of the inner peripheral approximately in synchronism with the rotor 4 surface of the housing, in other words, in ec- by the frictional force with respect to the pins centric fashion with respect to the rotor 100 13 and 13. Since the rotation of the journal whereby the radial movement thereof is debearings 45a and 45b is effected in a floated fined, and the vane rotates in non-contact fashion by a great dynamic pressure produced with the housing. In that case, the bearings in a fluid layer between the annular recesses are also rotated approximately in synchronism 15a and 15b on the housing side by the dy with the rotor by the contact of the projecnamic pressure producing grooves 46 and 47, tions of the vane, and therefore the relative the sliding resistance is very small. For these sliding movement between the bearings and reasons, it is possible to minimise the deter the projections of the vane can be minimised. ioration of the efficiency and abrasion resulting One example of the vane pump belonging to from the sliding resistance and sliding heat, the type 6 will be described hereinafter with 110 and the temperature of the discharged fluid reference to the drawings. also lowers.

In Figs. 26 and 27, journal bearings 45a Next, a pump shown in Fig. 29 uses ball and 45b formed of light-weight material such bearings 49a and 49b in place of the journal as aluminium are rotatably loosely mounted in bearings 45a and 45b in the pump shown in annular recesses 15a and 15b formed coaxi- 115 Fig. 26, and the ball bearings 49a and 49b ally with the inner peripheral surface of a are mounted in the annular recesses 15a and housing in the inner surfaces 1' and 2' of both 15b of the inner surfaces 1' and 2' of both end walls of the housing, and the opposed end walls of the housing. That is, the ball peripheral surface (outer peripheral surface) bearings 49a and 49b have their outer races and the opposed side with respect to the an- 120 50 and 50b fitted and secured to the inner nular recesses 15a and 15b in the journal peripheral surfaces of the annular recesses bearings 45a and 45b are formed with dy- 15a and 15b, and the pins 13 and 13 come namic pressure producing grooves 46 and 47 into contact with the inner peripheral surfaces as shown in Figs. 28(1) and 28(11). Pins 13 and of the inner races 51 a and 51b whereby the 13 of vanes 11 a, 11 b and 11 c are located on 125 inner races 51a and 51b rotate approximately the inner peripheral sides of the journal bear- in synchronism with the rotor 4, which pump ings 45a and 45b, and the pins 13 and 13 has the function substantially equal to the come into contact with the inner peripheral pump of Fig. 26.

surfaces of the bearings 45a and 45b during It is to be noted that since the rotor is rotation whereby the vanes 11 a, 11 b and 11 c130 eccentric the relative angle between the vane 8 GB2192939A 8 and the inner peripheral surface of the housing is very small whereby minimising the abra repeatedly varies as rotation proceeds, and sions of the annular race 16 (retainer plates therefore, in the event the appearance of the 15a, 15a), pins 13, etc. The aforesaid dy vane is defined as shown in the aforesaid namic pressure bearing mechanism can be re drawings, the locus of the end edge of the 70 placed, in addition to the already mentioned vane assumes an approximate elliptic shape. It spiral grooves 17, Rayleigh step grooves 18 is therefore desirable that the inner peripheral and herringbone grooves 18, by various surface of the housing is formed into a shape grooves, recesses and a combination of these corresponding to the aforesaid locus so as to which can produce dynamic pressure in a always maintain constant a clearance between 75 manner similar to the former.

the end edge of the vane and the inner per ipheral surface of the housing. Type 8 The vane pump described above is designed A vane pump belonging to this type 8 is so that the projections provided on the oppo- characterised by the provision of means for site side ends of the vane are placed in con- 80 defining an appearance of vanes toward the tact with the inner peripheral surface of the inner peripheral surface of the housing, bearings provided coaxial with the inner per- wherein small-diameter bosses coaxial with ipheral surface of the housing and rotatably to the inner peripheral surface of a housing are define the radial movement thereof so that the projected internally of both end walls of the vane may be rotated in non-contact with the 85 housing to define a backward movement of housing as described above. Therefore, it is the vanes into the vane grooves. With this, possible to minimise the deterioration of the when the rotor stops, the inner end edges of pump efficiency and te advance of abrasion the vanes come into contact with the outer resulting from the sliding resistance and the peripheral surfaces of the bosses to check the high sliding heat and to lower the temperature 90 excessive retraction of the vanes into the vane of fluids discharge from the pump, this exhi- grooves, thus preventing an occurrence of a biting excellence, performances for use with sudden appearance of the vanes at the time various apparatuses such as a supercharger in of start. For more details, see Figs. 26 and the engine, a compressor in a freezing cycle, 29 and the description thereof.

and the like. 95 Type 9 Typ e 7 A pump belonging to the final type is char A vane pump belonging to this type 7 has a acterised in that retainer rings with which dynamic pressure bearing mechanism provided vanes are engaged to define an appearance of on the end or peripheral surface of a retainer, 100 vanes toward the inner peripheral surface of a and particularly being characterised in that said housing are provided coaxially with the inner dynamic pressure bearing mechanism cornperipheral surface of the housing internally of prises a groove or recess capable of produc- the opposite end walls of the housing so that ing dynamic pressure such as a spiral groove, they may be rotated, and said retainer rings a Rayleigh groove or a herringbone groove or 105 and the rotor may be rotatively connected by a recess or a combination of the aforesaid means of a cam. An object of the pump is to grooves and the recess. rotate the retainer rings rotatively connected One example of a vane pump belonging to to the rotor through the cam in synchronism this type 7 will be described hereinafter with with the rotor to minimise an amount of slid reference to the drawings. The outer ends of 110 ing movement resulting from the engagement the retainer rings 16a and 16b mounted as between the annular race and the projections.

shown in Fig. 30 opposed to the inner side of One example of the vane pump belonging to the housing 1 are formed with spiral grooves the afore type 9 will be described below with 52 as shown in Fig. 31, and the outer periphreference to the drawings.

eral surfaces thereof formed with Rayleigh 115 In Figs. 34 to 36, a front housing indicated step grooves 53 and herringbone grooves 54 at 1 and a rear housing indicated at 2, which as shown in Figs. 32 and 33. The dynamic are formed of non-ferrous metal such as alu pressure bearing mechanism is provided to minium having a small coefficient of thermal smoothly rotate the retainer rings 16a and expansion, are integrally secured to each other 16b with respect to the housing 1. 120 by means of bolts 3. A rotor 4 made of iron The pins 13 are slidably rotated while being eccentrically inserted into an inner peripheral pressed against the outside diameter side by space 5 of the housing is extended through the centrifugal force within the annular race 16 both the housings 1 and 2 through a ball of the retainer plates 15a and 15b but the bearing 7a held by a fixed ring 6 in anti-sli retainer plates 15a and 15b follow the pins 125 pout fashion in an axial shoulder of the front 13 and rotate since the retainer plates 15a housing 1 and a ball bearing 7b held by a and 15b are in the state in which they may bearing cover 8 in anti- slipout fashion in an be smoothly rotated by the dynamic pressure axial shoulder of the rear housing 2 and is bearing mechanism. The relative sliding speed rotatably mounted on a rotational shaft 10 to between the pins 13 and the annular race 16 130which a drive force is transmitted from a pul- GB2192939A 9 9 ley 9. Plate-lie vanes 11 principally made of aforesaid displacement.

a carbon material having an excellent slidability In the above-described arrangement, when are disposed to be radially projected and re- the rotational shaft 10 and the rotor 4 are tracted in vane grooves 12., respectively, rotated by the drive force from the pulley 9, which are formed in the form of a depression 70 the vanes 11 rotate accordingly, and the equally spaced apart so as to peripherally di- retainer rings 16a and 16b rotatively con vide the outer peripheral side of the rotor 4 nected to the rotor 4 by the cams 56a and into three sections, on the rotor. Projections 56b also rotate. Here, the appearance of the 13 and 13 are provided on opposite side vanes 11 toward the inner peripheral sur- ends in an axial direction of each vane 11, 75 face 1" of the housing by the centrifugal force and a sliding member (not shown) made of is defined by the engagement between the resin having excellent slidability and abrasion projections 13 and 13 of the vanes 11 and resistance is slipped over the projection 13 as the arched grooves 55a and 55b of the re needed. Retainer rings 16a and 16b formed of tainer rings 16a and 16b, as previously mennon-ferrous metal such as aluminium and hav- 80 tioned, and therefore the vanes 11 rotate in ing arched grooves 55a., 55b peripherally the state leaving a fine clearance with respect equally divided into three sections are rotata- to the inner peripheral surface 1" of the hous bly mounted through ball bearings 18a and ing. Also, the loci of the arched grooves 55a 18b, respectively, in annular recesses 15a and and 55b are in the coaxial relation for the 15b formed coaxial with the inner peripheral 85 inner peripheral surface 1' of the housing while surface 1" of the front housing 1 in the inner in the eccentric relation for the rotor 4, and surfaces 1' and 2' of the front housing 1 and therefore, with the aforesaid rotation, the rear housing 2. The projections 13 and 13 vanes 11 radially slidably move within the provided on the vanes 11 are slidably en- vane grooves 12 of the rotor 4 for repeated gaged with the arched grooves 55a., 55b 90 projection and retraction, and the volumes of .. of the retainer rings 16a and 16b to define the working spaces 5 defined by the housings the radial movement of the vanes 11 dur- 1, 2, the rotor 4 and the vanes 11 repeat- ing rotation so as to always maintain a fine edly increase and decrease to effect suction clearance between each of the end edges 11' and discharge of fluids.

and the inner peripheral surface 1" of the 95 In a series of operation as described above, housing. Cams indicated at 56a 56b are the vanes 11 are not in contact with the provided to rotatively connect the rotor 4 and inner peripheral surface 1' of the housing, and the retainer rings 16a and 16b at their op- therefore, there occurs no power loss and posed ends, and pins 57a and 57b of the generation of high heat due to the sliding tor cams 56a and 56b, respectively, are fitted 100 que, early advance of abrasion, and the like; through ball bearings 59a and 59b in positions the amount of sliding between the projections where the opposite ends of the rotor 4 are 13, 13 of the vanes 11 and the arched peripherally equally divided into three sections grooves 55a, 55b is restricted to the range while the other pins 58a and 58b are fitted approximately twice the amount of eccentricity through ball bearings 60a and 60b in positions 105 A; and the relative sliding speed thereof is where the ends of the retainer rings 16a and small since the retainer rings 16a and 16b 16b, respectively, are peripherally equally div- rotate in synchronism with the rotor 4.

ided into three sections. The distance be- Next, the pump shown in Fig. 37 is different tween the centres of the pins 57a, 57b and from those shown in Figs. 34 to 36 in that 58a, 58b equals an amount of eccentricity of 110 the projections 13 and 13 provided on the the rotor 4 with respect to the inner periph- opposite side ends in the axial direction of the eral surface 1" of the housing, in other words, vanes 11 are slidably engaged with the in an amount of eccentricity A of the rotor 4 terior of the annular grooves 61a and 61b and the retainer rings 16a and 16b, that is, formed in the retainer rings 16a and 16b.

the pins 57a, 57b and 58a, 58b maintain their 115 Also in this case, the retainer rings 16a and same angular positional relation with each 16b are rotated in synchronism with the rotor other and rotate on the circumference of the 4 through the cams 56a 56b whereby same diameter with eccentricity of said the projections 13 and 13 are merely slidably amount A. Incidentally, the loci of the vane moved with the annular grooves 61a and 61b grooves 12 and the loci of the arched 120 in the range of length about twice the amount grooves 55a., 55b are naturally in the ec- of eccentricity of the rotor 4, and the relative centric relation, and therefore, in the case sliding speed thereof is exactly the same as where the retainer rings 16a and 16b are syn- that of Fig. 34.

chronously rotated by the cams 56a., 56b Incidentally, a bottom space 12S of each 60., the projections 13 and 13 of the vanes 11 125 vane groove 12 which is the inside of each are displaced, with the rotation, in the range vane has a volume which repeatedly increases of the length about twice the amount of ec- and decreases with the projection and retrac centricity A relative to the arched grooves 55a tion of the vane 11, and accordingly, the and 55b. Accordingly, the arched grooves 55a pressure within the bottom space 12S acting and 55b are set to the length above the 130as a back pressure on the vane 11 also re- GB2192939A 10 peatedly varies. This will be further described. sliding heat and the early advance of abrasion In rotation of the vane 11 from the top T and which can lower the temperature of the toward the bottom B, the vane 11 is in the fluid discharged out of the pump. The pump is stage in which the vane projects from the extremely suitable for use with the superchar- vane groove 12, and the volume of the bot- 70ger of the engine, the compressor of the tom space 12S gradually enlarges and the in- freezing cycle, and the like.

ternal pressure lowers, while in rotation of the

Claims

vane 11 from the bottom B toward the top T, CLAIMS the vane 11 is in the

stage in which the vane 1. A vane pump comprising a rotor rotata retracts into the vane groove 12, and the vol- 75 bly supported in eccentric fashion in the inner ume of the bottom space 12S gradually con- peripheral space of a housing, and plate-like tracts and the internal pressure rises. That is, vanes disposed capable of being projected the change in the internal pressure of the bot- and retracted into a plurality of vane grooves tom space 12S resulting from the rotation in said rotor, wherein repeated variations in always exerts in the direction of impeding the 80 volumes of working spaces between the projection and retraction operation of the vane vanes resulting from rotation of the rotor and 11, and thus there is a possibility of deterior- the vanes are utilised to suck a fluid from one ating the pump efficiency. In the pump as de- side and discharge it toward the other, char scribed, the annular grooves 61a and 61b acterised in that projections such as pins are provided for engagement of the projections of 85 provided on opposite ends of each of the the vanes 11 have the advantage by which vanes, and annular races are formed internally such unstable elements as described above of the housing, said annular races being coax are overcome. That is, since the axial side ial with the inner peripheral surface of the ends of the bottom spaces 12S open to the housing, said annular races being slidably en- annular grooves 61a and 61b, the fluid within 90 gaged by said projections to vary the extent the bottom space 12S whose volume is being to which the vanes project from the vane contracted freely flows into the other bottom grooves as the rotor rotates.

space 12S whose volume is being enlarged
2. A pump comprising a stator, defining a through the annular grooves 61a and 61b, so generally cylindrical chamber, having circumfer- as to minimise the change in the internal pres- 95 entially spaced inlet and outlet ports, a rotor sure. mounted in said chamber for rotation about an It is noted in the vane pump that in view of axis extending parallel to but spaced from the the feature in which the rotor is eccentric with axis of the chamber, said rotor having a plu respect to the housing, the relative angle rality of circumferentially spaced radially ex formed between the inner peripherl surface of 100 tending slots each accommodating a vane, the housing and the vane repeatedly varies each vane being urged by centrifugal force, with the rotation thereof. Accordingly, in the when the rotor rotates along its corresponding pump as described above, where the appear- slot towards the circumferential wall of the ance of the vanes 11 caused by the engage- chamber, so that the vanes divide the cham- ment between the projections 13, 13 and the 105 ber into separate compartments which change arched grooves 55a, 55b or the annular in volume as the rotor rotates to create a grooves 61a, 61b is defined on the relatively pump action between the inlet and outlet inner peripheral side, the locus of the end ports, and cam means for constraining the edge 11' of the vane assumes an approximate movement of each vane along each slot so as elliptic configuration. Therefore, it is desirable 110 to maintain a substantially constant clearance that the inner peripheral surface 'I" of the between the vane and the circumferential sur- 1 housing is formed into a shape corresponding face of the chamber.

to said locus to always maintain constant a
3. A pump according to Claim 2 wherein clearance between the end edge 11' of the said cam means comprises a pin extending vane and the inner peripheral surface 1" of the 115 from an axial end of a said vane and engaging housing. a cam groove in an adjacent axial end wall of As described above, the vane pump belong- said chamber.

ing to the aforesaid type is designed so that
4. A pump according to Claim 3 wherein the vanes are rotated in non-contact with the the said pin supports a bearing which engages housing by the provision of the retainer rings 120 said cam groove.

which define the appearance of the vanes to-
5. A pump according to Claim 3 wherein ward the inner peripheral surface of the hous- said pin engages an arcuate slide which is in ing, and the retainer rings are rotatively con- slidable engagement with said cam groove.

nected for synchronous rotation with the rotor
6. A pump substantially as hereinbefore de by means of the cams to minimise the sliding 125 scribed with reference to any one of Figs. 1 movement resulting from the engagement be- to 37 of the accompanying drawings.

tween the retainer rings and the vanes, thus Published 1988 at The PatentOffice, State House, 66171 High Holborn, exhibiting the excellent advantages which can London WC 1 R 4TP. Further copies may be obtained from prevent the deterioration of the pump effici- The Patent Office, Sales Branch, St Mary Cray, Orpington, Kent BR5 3RD.

ency due to the sliding resistance and high Printed by Burgess & Son (Abingdon) Ltd. Con. 1/87.