EP1183468B1 - High pressure pump with improved hub - Google Patents

Description

The present invention relates to a high-pressure pump with improved hub.

It applies in particular to a high-pressure pump for supplying fuel to an internal combustion engine of a motor vehicle. In this case, the transferred liquid is the fuel.

Already known in the state of the art a high pressure pump for pumping a first liquid, said transferred liquid, of the type comprising a main unit for pumping the transferred liquid operated by a secondary pumping unit of a second liquid, said working liquid, the secondary unit comprising a hub rotatably mounted in a bearing housing, and at least one working liquid compression piston, displaceable substantially parallel to the axis of rotation of the hub, resiliently biased against a platter bias actuation of this piston, carried by the hub.

The hub comprises a peripheral cylindrical surface rotational guide in the housing, extended by an axial positioning shoulder of the hub in the housing, the peripheral guide surface and the axial positioning shoulder cooperating respectively with complementary means for guiding rotation and complementary axial positioning means carried by the housing, the axial positioning shoulder being urged in abutment against the complementary axial positioning means carried by the housing by the elastic return force of the piston and the pressure of the working liquid in contact with the bias tray.

A pump of this type is described for example in WO 97/47883.

The hub of the pump described in this document is rotatably mounted in the housing by means of ball bearings for guiding rotation and axial positioning of the hub in the housing. These ball bearings have the disadvantage of being bulky, relatively heavy and expensive, and sometimes noise sources.

The object of the invention is to propose a high-pressure pump of the aforementioned type having means for guiding in rotation and for axial positioning of the hub in the housing that is effective, simple and compact.

To this end, the subject of the invention is a high-pressure pump, of the aforementioned type, characterized in that the peripheral guiding surface is formed by an inner surface of a sleeve in which the bias plate and said at least one plate are housed. compression piston of the working liquid.

• le manchon comporte une bague rapportée sur ce manchon et dont une face forme l'épaulement de positionnement axial,
• le manchon est formé par un organe tubulaire étagé en une seule pièce dont la surface externe détermine la surface périphérique de guidage et l'épaulement de positionnement axial,
• le manchon est prolongé à une extrémité par une collerette délimitant l'épaulement de positionnement axial,
• les moyens complémentaires de guidage en rotation comprennent une surface cylindrique de portée en contact glissant avec la surface périphérique de guidage du manchon et les moyens complémentaires de positionnement axial comprennent une surface plane de portée en contact glissant avec l'épaulement ;
• la surface cylindrique de portée est formée par la surface interne d'une chemise du boîtier, la surface plane de portée étant formée par une face d'une rondelle disposée à une extrémité de la chemise ;
• la surface cylindrique de portée est formée par la surface interne d'un manchon, la surface plane de portée étant délimitée par une collerette prolongeant une extrémité du manchon ;
• les moyens complémentaires de guidage en rotation comprennent des aiguilles de roulement, portées par le boîtier, s'étendant sensiblement parallèlement à l'axe de rotation du manchon, et les moyens complémentaires de positionnement axial comprennent des aiguilles de roulement portées par le boîtier, s'étendant sensiblement radialement par rapport à l'axe de rotation dudit manchon ;
• le liquide transféré est un carburant pour moteur à combustion interne de véhicule automobile.

According to other characteristics of this pump:

• the sleeve comprises a ring attached to this sleeve and one face of which forms the axial positioning shoulder,
• the sleeve is formed by a staggered tubular member in one piece whose outer surface determines the peripheral guide surface and the axial positioning shoulder,
• the sleeve is extended at one end by a flange delimiting the axial positioning shoulder,
• the complementary rotation guiding means comprise a cylindrical bearing surface in sliding contact with the peripheral surface for guiding the sleeve, and the complementary axial positioning means comprise a flat bearing surface in sliding contact with the shoulder;
• the cylindrical bearing surface is formed by the inner surface of a casing of the casing, the flat bearing surface being formed by a face of a washer disposed at one end of the casing;
• the cylindrical bearing surface is formed by the inner surface of a sleeve, the flat bearing surface being delimited by a flange extending one end of the sleeve;
• the complementary rotation guiding means comprise bearing needles, carried by the housing, extending substantially parallel to the axis of rotation of the sleeve, and the complementary axial positioning means comprise bearing needles carried by the housing, extending substantially radially with respect to the axis of rotation of said sleeve;
• the transferred liquid is a fuel for an internal combustion engine of a motor vehicle.

• la figure 1 est une vue de face d'une pompe à haute pression selon l'invention ;
• la figure 2 est une vue en coupe suivant la ligne 2-2 de la figure 1 ;
• la figure 3 est une vue en coupe suivant la ligne 3-3 de la figure 1 ;
• la figure 4 est une vue de détail de la figure 2 dans laquelle le plan de coupe a été légèrement décalé de façon à passer par l'axe de la vis représentée sur ces figures 2 et 4 ;
• la figure 5 est une vue de détail de la partie entourée 5 de la figure 3 montrant un bouchon d'obturation de moyens de remplissage d'un réservoir de la pompe dans une position de pré-obturation ;
• la figure 6 est une vue similaire à la figure 5 représentant une première variante du bouchon ;
• la figure 7 est une vue similaire à la figure 3 représentant une seconde variante du bouchon ;
• les figures 8 à 11 sont des vues similaires à la figure 2 représentant quatre variantes respectivement d'un moyeu de la pompe selon l'invention.

The invention will be better understood on reading the following description given solely by way of example and with reference to the appended drawings in which:

• Figure 1 is a front view of a high pressure pump according to the invention;
• Figure 2 is a sectional view taken along line 2-2 of Figure 1;
• Figure 3 is a sectional view taken along line 3-3 of Figure 1;
• Figure 4 is a detail view of Figure 2 in which the section plane has been slightly shifted to pass through the axis of the screw shown in Figures 2 and 4;
• Fig. 5 is a detail view of the circled portion of Fig. 3 showing a closure cap of means for filling a reservoir of the pump in a pre-sealing position;
• Figure 6 is a view similar to Figure 5 showing a first variant of the plug;
• Figure 7 is a view similar to Figure 3 showing a second variant of the plug;
• Figures 8 to 11 are views similar to Figure 2 showing four variants respectively of a hub of the pump according to the invention.

FIGS. 1 to 3 show a high-pressure pump according to the invention, designated by the general reference 12. In the example described, the pump 12 is intended for supplying high-pressure fuel to a combustion engine. internal combustion of a motor vehicle. The pump 12 is thus intended to pump a first liquid, namely fuel in the example described, called transferred liquid.

In Figure 1 there is a connector 14 for connecting the pump 12 to a fuel tank.

Referring more particularly to FIGS. 2 and 3, it can be seen that the pump 12 comprises a casing 16 of generally cylindrical shape, of axis X, in which are arranged a main unit 18 for pumping fuel and a secondary unit 20 for pumping. a second conventional liquid, for example a mineral oil, said working liquid. The main unit 18 is actuated by the secondary unit 20 according to general principles of conventional operation described for example in WO 97/47883.

The housing 16 comprises a body 22, of generally cylindrical shape, surrounding the secondary unit 20, and a lid 24, of generally cylindrical shape, surrounding the main unit 18. The housing body 22 and the cover 24 form respectively two ends opposite of the housing 16.

The housing body 22 is connected to the cover 24 by at least one screw 26, for example three screws 26. Each screw 26, preferably made of steel, extends substantially parallel to the axis X. A screw 26 will be described in more detail. detail later.

Inside the housing 16, the main unit 18 is separated from the secondary unit 20 by a separation disc 28 centered substantially on the X axis. This disc 28 is preferably made of steel or cast iron.

The main unit 18 comprises at least one flexible membrane 30 for fuel pumping, for example three membranes 30 as in the example illustrated. It will be noted that only two membranes 30 are shown in the figures, in particular in FIG.

The membrane 30 separates a fuel pumping chamber 32, arranged in the main unit 18, from a working liquid compression chamber 34, arranged in the secondary unit 20. The volume of the pumping chamber 32 is variable . The compression chamber 34 is partially formed in the separation disc 28.

Each pump chamber 32 is associated with a valve 36 for fuel suction and a valve 38 for fuel delivery. These valves 36, 38, of conventional structure and operation, are carried by a body 40 housed in the cover 24 between a bottom of the latter and the separating disc 28.

For the sake of lightening the pump 12, the body 22 of the housing, the cover 24 and the valve body 40 are made of aluminum or aluminum-based alloy or another equivalent light metal.

The valves 36, 38 are connected in a manner known per se to the corresponding pumping chamber 32 and a safety valve 42 of conventional structure and operation.

Conventionally, each membrane 30 is movable between a first position of maximum volume of the pumping chamber 32, as shown in particular in FIGS. 2 and 3, and a second position of minimum volume of this pumping chamber (not shown in FIG. the figures). The movements of the membrane 30 are imposed in particular by the secondary unit 20 and control the opening and closing of the valves 36, 38 of suction and discharge of fuel.

Each membrane 30 is constantly resiliently biased towards its first position by a spring 44, said diaphragm spring.

Each valve 36, 38 communicates, on the one hand, with a fuel suction chamber 46 and, on the other hand, a fuel delivery chamber 48. The suction chamber 46 is connected in a manner known per se to the fuel supply connection 14.

The suction chambers 46 and the fuel delivery chamber 48 are delimited, at least in part, by facing surfaces 50, 52 of generally cylindrical shape, with an axis substantially coinciding with the axis X. A first surface 50 forms an inner surface of the cover 24. The second surface 52 forms a peripheral surface of the valve body 40.

The facing surfaces 50, 52 comprise two complementary shoulders 50E, 52E resting between them so as to form a sealing plane separating the suction chamber 46 and discharge chamber 48. This joint plane is substantially perpendicular to the axis X. Shoulders 50E, 52E form an effective metal-to-metal seal.

It will be noted that the suction chamber 46, in which the pressure is lower than in the delivery chamber 48, is delimited by the bottom of the cover 24, the thickness of which is relatively small. By against the discharge chamber 48 is delimited by a peripheral wall of the lid 24 thicker than the bottom of the lid, so as to withstand the high pressure reached by the fuel flowing in the discharge chamber.

The secondary unit 20 comprises a working liquid compression piston 54 associated with each membrane 30 and intended to move this membrane 30 between its two positions. Thus, in the example described, the secondary unit 20 comprises three pistons 54 of which only two are visible in the figures, in particular in FIG.

The piston 54 is slidably mounted in a body 56, preferably of steel or cast iron, so as to be displaceable substantially parallel to the axis X. The piston 54 extends between the chamber 34 for compressing working liquid, arranged partly in the piston body 56, and a reservoir 58 of working liquid.

The end of the piston 54, external to the body 56 of the piston, is biased resiliently by a spring 59 in contact with a rolling stop, for example a needle stop 60, carried by a bias plate 62 for actuating the pistons 54 This bias plate is carried by a hub 64 of the secondary unit 20. This hub 64 is rotatably mounted about the X axis in the bearing housing body 22. The bias plate 62 rotates about the X axis together with the hub 64, the latter being connected to conventional drive means by an Oldham-type seal 66. The sealing of the working liquid between the housing body 22 and the hub 64 is provided by conventional means including an annular seal 67 of elastomer. The hub 64 will be described in more detail later.

It will be noted that the separation disc 28 and the piston body 56 form an intermediate assembly EI axially gripped between a skirt 22J of the body body 22, internal to the cover 24, and the body 40 of the valve. Moreover, with particular reference to FIG. 4, it can be seen that each screw 26 is provided with a head 26T and a threaded body 26C. The head 26T is supported on a passing seat 68 formed in the housing body 22. The threaded body 26C is screwed into a threaded orifice 70 formed in an ear 72 integral with the cover 24. As a result, the housing body 22, the intermediate assembly EI and the valve body 40 are clamped between the head 26T of the screw and the joint plane materialized by the shoulders 50E, 52E.

Preferably, the axial dimension L1 of the intermediate assembly EI is substantially equal to the length L2 of the portion of the body 26C of the screw extending between the head 26T of this screw and the threaded orifice 70. In this way, the expansions of the different materials, namely, on the one hand, aluminum or light metal and, on the other hand, steel or cast iron, are substantially identical inside and outside the casing 16 .

Referring again to FIGS. 2 and 3, it can be seen that the piston 54 is provided with an axial bore 74 through which the working liquid can flow between the reservoir 58 and the compression chamber 34. A first end of the bore 74, inside the piston body 56, communicates permanently with the compression chamber 34. The second end of the bore 74, external to the piston body 56, communicates permanently with the reservoir 58.

Preferably, the bore 74 is stepped and comprises a section 74A of large diameter, opening into the compression chamber 34, and a section 74B of small diameter, opening into the reservoir 58.

A ball, forming a valve 76, is housed in the section 74A of large diameter so as to be displaceable, on the one hand, between a shoulder E74, separating the sections 74A and 74B, forming a closing seat of the valve 76, and on the other hand, a stop 78 for limiting the opening stroke of this valve 76.

The valve 76 opens as soon as the pressure of the working liquid in the tank 58 exceeds that of the working liquid in the compression chamber 34. In the opposite case, the valve 76 closes so as to close the bore 74.

For the proper functioning of the pump 12, the stiffness of the spring 44 of the diaphragm 30 associated with the piston 54 is dimensioned so that the spring 44 maintains the working liquid contained in the compression chamber 34 at an overpressure relative to the working fluid contained in the reservoir 58, as long as the membrane 44 has not reached its first position of maximum volume of the pumping chamber 32.

Some particular characteristics of the operation of the main units 18 and secondary 20 pumping will be indicated below, the main unit 18 operating according to the principles of a positive displacement pump.

When the bias plate 62 pushes the piston 54 into the piston body 56 (displacement of the piston 54 to the right, considering FIGS. 2 and 3), the working liquid contained in the compression chamber 34 is compressed (in overpressure relative to the liquid contained in the tank 58), so that the valve 76 closes and the flexible membrane 30 moves to its second position of minimum volume of the pumping chamber 32. This causes, as is conventional, the discharge of the fuel at high pressure in the delivery chamber 48.

When the bias plate 62 allows the piston 74 to move in a direction opposite to the preceding one (to the left considering FIGS. 2 and 3), under the effect of the return spring 59, the membrane 30 is returned by the spring 44 in its first position of maximum volume of the pumping chamber 32. This causes, as is conventional, the suction of the fuel, from the suction chamber 46, in the pumping chamber 32.

Note that the membrane spring 44 allows the automatic return of the membrane 30 in its first position, this even in case of absence of fuel in the main pumping unit 18. Moreover, when the piston 54 moves towards the left considering FIGS. 2 and 3, given the leakage of working fluid between the compression chamber 34 and the tank 58, the membrane 30 reaches its first position before the piston 54 completes its stroke to the left. Therefore, once the membrane 30 reaches its first position, the pressure of the working liquid in the compression chamber 34 decreases relative to that of the working liquid in the reservoir 58, causing the valve 76 to open and replenishing the compression chamber 34 in working fluid so as to compensate for leaks.

Described below, with particular reference to FIGS. 3 and 5, are simple and effective means for completely filling the reservoir 58 with working fluid.

These filling means comprise a filling neck 80, connected to the reservoir 58, closable by a stopper 82.

In the example illustrated in FIGS. 3 and 5, the plug 82 is intended to cooperate by screwing with the neck 80. The plug 82 comprises a blind hole 84, substantially axial, communicating via a hole 86 of the plug , substantially radial, with a circumferential recess 88 of the plug axially extended by a closure surface 90 of this plug intended to cooperate with a closure seat 92 formed in the end of the neck 80 near the reservoir 58.

Preferably, the closure surface 90 and the closure seat 92 have generally conical shapes, the closure surface 90 converging towards the closure seat 92.

The plug 82 is movable in the neck 80, by screwing, between a. pre-closing position of the reservoir 58, in which the closure surface 90 is spaced from the seat 92, above this seat 92, as shown in FIG. 5, and a closed position of this reservoir 58 in which the sealing surface 90 is in sealing contact with the seat 92, as shown in FIG. 3.

The neck 80 is likely to contain too much working fluid in excess of the reservoir, the level N of this overflow extending into the neck 80 above the seat 92.

Note that when the plug 82 is in its pre-sealing position, the peripheral recess 88 of this plug communicates with the reservoir 58, so that the blind hole 84 forms a receptacle for the overflow of working liquid. Moreover, in the presence of the overflow in the neck 80, the plug 82 is movable in this neck between its pre-sealing and sealing positions.

To move the cap 82, the latter is provided with an operating head 82T through which opens the open end of the blind hole 84. The head 82T is delimited by a polygonal inner surface 821 for the operation of the plug 82 to the using a classic tool.

Alternatively, the operating head 82T may be delimited by a polygonal outer surface 82E as shown in Figure 6, for the operation of the plug 82 with a conventional tool.

The plug 82 carries a peripheral ring seal 93 positioned axially between the head 82T and the recess 88. This seal 93 seals between the neck 80 and the plug 82 above the recess 88.

The plug 82 makes it possible to fill the reservoir 58 under vacuum as follows.

Initially, the plug 82 is screwed into the neck 80 in its pre-sealing position as shown in FIG.

To fill the reservoir 58 with working fluid, the vacuum is evacuated in this reservoir, using conventional means, and then the working liquid is introduced through the blind hole 84 of the plug. In this way, the working liquid flows into the tank 58 while circulating in the blind hole 84, the radial bore 86 and the recess 88.

The filling of the reservoir 58 is continued until an overflow remains in the neck 80 and the blind hole 84, as shown in FIG.

Finally, in the presence of the overflow, the plug 82 is moved by screwing to its closed position as shown in FIG. 3. The reservoir 58 is then isolated from the filler neck 80, the quantity of working liquid remaining. in the blind hole 84 being easily discharged through the end of the blind hole 84 opening through the actuating head 82T.

Referring to FIG. 3, it will be noted that the reservoir 58 is connected to conventional means 94 for compensating for the expansion of the working liquid contained in the reservoir 58. These means comprise a flexible membrane 96 separating a channel 98 for communicating the membrane 96 with the working liquid of the reservoir 58 and a clearance space 100 of the membrane 96 protected by a shell 102 of generally hemispherical shape. The membrane 96 is deformed as a function of the variations in the volume of working liquid contained in the reservoir 58.

FIG. 7 shows an alternative embodiment of the plug 82.

In this case, the plug 82 comprises a ball 104 that can be displaced by force between a pre-sealing position of the reservoir 58, as shown in phantom in FIG. 7, and a closed position of this reservoir 58, as represented in solid lines in this figure 7.

The surface of the ball 104 forms the sealing surface intended to cooperate sealingly with the seat 92 of the neck.

The closure of the filling neck 80 by means of the ball 104 is carried out as follows.

In the presence of too much working fluid, whose level N is shown in phantom in FIG. 7, the ball 104 is placed in its pre-sealing position. as shown in phantom in this figure 7. Then, the ball 104 is forced into the neck 80 so as to press against the seat 92, as shown in solid lines in FIG.

It will be noted that during the force displacement of the ball 104 between its pre-closing and closing positions of the reservoir 58, the overflow of working liquid, forced into the reservoir 58 under the effect of displacement. of the ball 104, is compensated by the deformation of the membrane 96 of the expansion compensation means 94, as shown in FIG. 7.

The hub 64 will be described below in greater detail with reference to FIG.

In the example illustrated in this FIG. 3, the hub 64 comprises a sleeve 106, of axis coinciding with the axis X, in which the bias plate 62 is housed.

The hub 64 also comprises a ring 108 fixed on the outer surface of the sleeve 106.

The outer surface of the sleeve 106 forms a cylindrical peripheral surface SG for guiding the hub in rotation in the body body 22. One face of the ring 108 forms a shoulder FE axial positioning of the hub 64 relative to the housing body 22.

Furthermore, the housing body 22 has a liner 110 whose inner surface forms a cylindrical surface SP in sliding contact with the peripheral guide surface SG of the hub.

The casing body 22 also includes a washer 112, disposed at one end of the casing 110, provided with a face forming a flat bearing surface FP in sliding contact with the shoulder FE of the hub.

The jacket 110 and the washer 112 are fixed in a manner known per se on the housing body 22 and are made of conventional materials, preferably of low coefficient of friction.

It will be noted that the shoulder FE of the hub 64, extending the guide surface SG of this hub, is urged in abutment against the bearing surface FP of the body body 22 by the elastic force of the pistons 54 in contact with the stop with needles 60 as well as by the pressure of the working liquid in contact with the bias plate 62.

According to a first variant shown in FIG. 8, the cylindrical bearing surface SP is formed by the internal surface of a sleeve 114, carried by the body 22 of housing, provided with an end extended by a flange 116 defining the flat surface FP range.

According to a second variant shown in FIG. 9, the peripheral guiding surface SG of the hub is formed by the external surface of a sleeve 118, in which the bias plate 62 is housed, provided with an extended end by a flange 120 delimiting the axial positioning shoulder FE of the hub. The sleeve 118 of the hub cooperates with a sleeve 114 secured to the body body 22 of the type shown in FIG.

According to third and fourth variants shown in FIGS. 10 and 11 respectively, the peripheral guiding surface SG and the axial positioning shoulder FE of the hub are formed by the external surface of a stepped tubular member 122, in one piece, in which is housed the bias plate 62. The stepped member 122 can be easily manufactured in a conventional manner, including stamping, processing and grinding.

In the third variant shown in FIG. 10, the stepped member 122 is in sliding contact with a cylindrical surface SP and a plane bearing surface FP arranged on elements similar to those shown in FIG.

In the fourth variant shown in Figure 11, the peripheral guide surface SG of the stepped member 122 is in contact with rolling needles 124 extending substantially parallel to the axis X, and the axial positioning shoulder FE is in contact with rolling needles 126, extending substantially radially with respect to the X axis.

The needles 124, 126 are carried by cages 128, 130 fixed in a manner known per se on the housing body 22.

Among the advantages of the invention, it will be noted that the means for guiding rotation and axial positioning of the hub relative to the pump housing according to the invention are simple, easy to manufacture and therefore inexpensive. In addition, these means are compact, relatively light and quiet.

Claims (9)

1. High-pressure pump for pumping a first liquid, called the transferred liquid, of the type comprising a main unit (18) for pumping the transferred liquid actuated by a secondary unit (20) for pumping a second liquid, called the working liquid, the secondary unit (20) comprising a hub (64) rotatably mounted in a casing (16) forming a bearing and at least one working liquid compression piston (54) movable substantially parallel to the rotation axis (X) of the hub and spring-loaded against a swash plate (62) for actuating the piston (54) carried by the hub (64), which comprises a peripheral cylindrical surface (SG) for guiding rotation in the casing (16) extended by a shoulder (FE) for axially positioning the hub in the casing (16), the peripheral guide surface (SG) and the axial positioning shoulder (FE) respectively cooperating with complementary rotation guide means (SP; 124) and complementary axial positioning means (FP; 126) carried by the casing (16), the axial positioning shoulder (FE) being spring-loaded against the complementary axial positioning means (FP; 126) carried by the casing (16) by the return spring force of the piston (54) and the pressure of the working liquid in contact with the swash plate (62), which pump is characterised in that the peripheral guide surface (SG) is formed by the external surface of a sleeve (106; 118; 122) in which the swash plate (62) and said at least one working liquid compression piston (54) are housed.
2. Pump according to claim 1, characterised in that the sleeve (106) includes a ring (108) attached to the sleeve (106) and one face whereof forms the axial positioning shoulder (FE).
3. Pump according to claim 1, characterised in that the sleeve is formed by a staggered one-piece tubular member (122) the external surface whereof determines the peripheral guide surface (SG) and the axial positioning shoulder (FE).
4. Pump according to claim 1, characterised in that the sleeve (118) is extended at one end by a flange (120) delimiting the axial positioning shoulder (FE).
5. Pump according to any one of claims 1 to 4, characterised in that the complementary rotational guide means comprise a cylindrical bearing surface (SP) in sliding contact with the peripheral guide surface of the sleeve (106; 118; 122) and the complementary axial positioning means comprise a plane bearing surface (FP) in sliding contact with the shoulder (FE).
6. Pump according to claim 5, characterised in that the cylindrical bearing surface (SP) is formed by the internal surface of a liner (110) of the casing (16) and the plane bearing surface (FP) is formed by one face of a washer (112) disposed at one end of the liner (110).
7. Pump according to claim 5, characterised in that the cylindrical bearing surface (SP) is formed by the internal surface of a sleeve (114) and the plane bearing surface (FP) is delimited by a flange (116) extending one end of the sleeve (114).
8. Pump according to any one of claims 1 to 4, characterised in that the complementary rotation guide means comprise roller bearing needles (124) carried by the casing (16) substantially parallel to the rotation axis of the sleeve (106; 118; 122) and the complementary axial positioning means comprise roller bearing needles (126) carried by the casing (16) substantially radially disposed relative to the rotation axis of said sleeve (106; 118; 122).
9. Pump according to any one of the preceding claims, characterised in that the transferred liquid is fuel for a motor vehicle internal combustion engine.

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