referring in more detail to the drawings , fig1 - 4 show a low and high speed needle valve assembly 20 having a biasing retainer 22 , embodying the present invention . mounting threadably to a carburetor body 24 are low and high - speed needle valves 26 , 28 which move longitudinally , via rotation , in and out of respective threaded ports 30 defined by the carburetor body 24 . air flowing through a throttling bore 31 extending through the carburetor body 24 mixes with a prescribed fuel quantity , or flow rate , controlled by the low and high speed needle valves 26 , 28 . the fuel flow rate within the carburetor body 24 is adjusted by threadably rotating the needle 32 within the respective port 30 either inward to reduce the fuel flow or outward from the carburetor body 24 to increase the fuel flow . the low and high - speed needle valves 26 , 28 each have a spring 34 and a shank or needle 32 . the spring 34 provides resistance against unintentional rotation of the needle 32 . the spring 34 concentrically encircles the needle 32 and is compressed axially between a radially extended head 36 of the needle 32 and the carburetor body 24 , the spring 34 engaging an inward facing annular surface 38 defined by the radially expanded head 36 . the axial constant force produced by the compression of the spring 34 provides the resistance which restrains rotation of the needle 32 by creating friction between the threads of the carburetor body 24 and the needle 32 within the port 30 . customarily , the low and high - speed needle valves 26 , 28 of each carburetor are adjusted and set at the factory by the engine manufacturer after the carburetor body 24 is mounted to a running combustion engine , not shown . if the fuel and air mixture is too lean , the running engine may over heat causing warranty concerns . if the fuel and air mixture is too rich , government regulatory emission requirements may be exceeded or violated . therefore , limiting adjustment capability by the end user of the engine of the low and high - speed needle valves 26 , 28 within an acceptable range is desirable . the engagement of known limiter caps 40 to the valves 26 , 28 establishes the end user adjustment range for fuel flow within the carburetor ( i . e . neither too rich nor too lean ). the limiter caps 40 are press fitted over the heads 36 of the low and high - speed needle valves 26 , 28 in the factory after the proper fuel flow settings are made . without the retainer assembly and after factory adjustment by the engine manufacturer , the press fitting of the limiter caps 40 to the heads 36 of either one or both of the needles 32 may unintentionally rotate , wobble or laterally shift the needles causing the factory setting and prescribed adjustment range of the needles 32 to be altered or changed . to feasibly solve this problem , the single retainer 22 of the present invention engages and laterally biases a shank 46 of each needle 32 which protrudes outward from the carburetor body 24 . preferably , the retainer 22 is axially aligned and disposed radially outward from the respective springs 34 . the lateral force exerted by the retainer 22 against the springs 34 causes the springs 34 to exert a lateral force against the shanks 46 of the needles 32 . the needles 32 , therefore , are skewed against , or tend to favor one side , of the respective ports 30 . the resultant friction between the springs 34 and the shanks 46 along with the increased friction between the threads of the needles 32 and ports 30 will assist the springs 34 to further resist any rotation of the needles 32 . that is , the axial force produced by the springs 34 is compounded by the lateral force produced by the retainer 22 . furthermore , the necessity of utilizing the spring 34 to resist rotation can be eliminated with a sufficiently strong or appropriately sized retainer 22 . in such an embodiment , the force produced by the retainer 22 is exerted directly on the shanks 46 of the low and high speed needle valves 26 , 28 . another feature of the retainer 22 is the elimination or reduction of needle tip 48 wobble within an orifice of the fuel flow channel of the carburetor body 24 , not shown . the wobble action of the tip 48 of the needle 32 is caused by machining tolerance limitations of the carburetor body 24 threads contained within port 30 and the mating threads of needle 32 . the resultant wobble can affect fuel flow causing a rough running combustion engine . the exertion of a lateral bias or force upon the shanks 46 of the needles 32 by the retainer 22 will produce a longitudinal stress and strain along the needle 32 . this causes the needle 32 to favor or even bear on one side of the orifice and thereby eliminates some or all of the adverse wobble effects . referring to fig2 - 4 , a first embodiment of the retainer 22 is illustrated as a clip retainer 50 which laterally engages both springs 34 of the respective low and high - speed needle valves 26 , 28 to laterally bias the projecting portions of the shanks 46 toward one another . an angled first leg 52 of the clip retainer 50 engages the spring 34 and thereby interconnects with a longitudinal outward surface 56 of the shank 46 of the low speed needle valve 26 , which faces outward with respect to the high - speed needle valve 28 . an angled second leg 54 of the clip retainer 50 engages the other spring 34 and interconnects with a longitudinal outward face 56 of the shank 46 of the high - speed needle valve 28 , which faces outward with respect to the shank 46 of the low - speed needle valve 26 . the clip retainer 50 laterally snap fits or is interference fitted about both the low and high - speed needle valves 26 , 28 . to assist in the snap fit , the distal ends 60 , 62 of the respective first and second legs 52 , 54 bend substantially radially outward with respect to the shank 46 of the respective low and high - speed needle valves 26 , 28 . referring to fig1 and 6 , a second embodiment of the retainer 22 is shown as a wedge retainer 64 . the wedge retainer 64 may take the form of a variety of shapes including an l - shape , an i - shape and preferably a t - shape . the wedge retainer 64 has a substantially planar primary member 66 which is wedged , via a snap fit , between and thereby engages the springs 34 of the low and high - speed needle valves 26 , 28 . the wedging effect causes the projecting portions of the shanks 46 to laterally bias outward from one another . providing the snap fit is an enlarged distal end 68 of the primary member 66 . the thickness of the distal end 68 is appreciably larger than the distance between the low and high speed needle valves 26 , 28 in the assembled state . the primary member 66 also has an enlarged base end 70 ensuring , when coupled with the enlarged distal end 68 , that the wedge retainer 64 has minimal lateral movement and remains wedged between the springs 34 or shanks 46 during end user adjustment rotation of the low or high - speed needle valves 26 , 28 . the primary member 66 with the enlarged distal and base ends 68 , 70 form the i - shape referred to above . the primary member 66 of the wedge retainer 64 engages the springs 34 on one side between the distal and base ends 68 , 70 and thereby interconnects with a longitudinal inward face 71 of the shank 46 of the low - speed needle valve 26 which radially faces generally toward the shank 46 of the high - speed needle valve 28 . likewise , the primary member 66 engages the other spring 34 on the other side and thereby interconnects with the longitudinal inward surface 71 of the shank 46 of the high speed needle valve 28 which faces substantially toward the shank 46 of the low - speed needle valve 26 . the wedge retainer 64 has a substantially planar first base member 72 extending substantially perpendicularly from the primary member 66 along the base end 70 . base member 72 is disposed generally tangentially with respect to the shank 46 of the low - speed needle valve 26 . the primary member 66 coupled with the first base member 72 form the l - shape referred to above . preferably , the wedge retainer 64 also has a substantially planar second base member 74 extending from the primary member 66 along the base end 70 , but in an opposite direction with respect to the first base member 72 . the second base member 74 lies generally tangentially to the shank 46 of the high - speed needle valve 28 . the first and second base members 72 , 74 lie substantially within the same imaginary plane and thereby compose an enlarged surface 76 upon which a force can be exerted to snap fit the wedge retainer 64 between the low - and high - speed needle valves 26 , 28 . the primary , first base and second base members 64 , 72 , 74 form the t - shape referred to above . referring to fig1 and 8 , a third embodiment of the present invention is shown wherein the retainer 22 is a band retainer 78 . like the clip retainer 50 , the band retainer 78 laterally bands or biases together the projecting portions of the shanks 46 of the respective low and high - speed needle valves 26 , 28 . the band retainer 78 encircles both the shanks 46 of the low and high - speed needle valves 26 , 28 and may be made of an elastic or plastic material which may also have a shrinking capability upon the application of heat . referring to fig1 and 10 a fourth embodiment of the retainer 22 is shown as being a triangular band retainer 79 having a slightly larger diameter or circumference than the band retainer 78 . the larger diameter enables the band retainer 79 to encircle not only the shanks 46 but also a pin 80 which rigidly protrudes outward from the carburetor body 24 . the pin 80 is preferably and substantially disposed at an equal distance from the low and high - speed needle valves 26 , 28 . as with band retainer 78 above , the triangular band retainer 79 can be made of the same material as the band retainer 78 . referring to fig1 and 12 , a fifth embodiment of the retainer 22 is shown as being a ring retainer 82 preferably made of a plastic material . the ring retainer 82 biases the projecting portions of the shanks 46 of the low and high - speed needle valves 26 , 28 similar to the wedge retainer 64 . the ring retainer 82 is concentrically disposed about the spring 34 and the shank 46 of either the low or high - speed needle valves 26 , 28 . the thickness of the ring retainer 82 wall is slightly larger than the distance between the needle valves 26 , 28 and is defined by a circumferential inward surface 84 and a circumferential outward surface 86 . because the radial distance between the inward surface 84 and the outward surface 86 is larger than the distance between the springs 34 , the ring retainer 82 laterally biases the projecting portions of the shanks 46 outward or away from one another . referring to fig1 , 13 - 15 , a sixth embodiment of the retainer 22 is shown as being a block retainer 88 . the block retainer 88 laterally displaces either one of the shanks 46 of the low and high - speed needle valves 26 , 28 . the block retainer 88 has a continuous curved surface 90 defining an angled bore 91 and extended between an inward perimeter 92 and an outward perimeter 94 . the inward perimeter 92 is centered about a centerline 96 of the respective hole 30 . the outward perimeter 94 is radially misaligned to the centerline 96 of the hole 30 . this mis - alignment forces the low or high - speed needle valves 26 , 28 to become laterally displaced . the non - displaced needle valve inserts within a pilot hole 98 ( shown in fig1 ) of the block retainer 88 which is centered about the centerline 96 of the other hole 30 . referring to fig1 , block retainer 88 ′ is shown wherein lateral displacement of both the low and high - speed needle valves 26 , 28 is achieved by replacement of the pilot hole 98 with another angled bore 91 . the bores 91 are preferably angled toward or away from one another and are preferably not parallel to one another . the opposing angles will help avoid misalignment of the block retainer 88 to the carburetor body 24 during assembly . also during assembly , an indexing feature 100 of the block retainer 88 mates with a mating indexing feature 102 ( shown in fig1 ) on the carburetor body 24 . preferably , the indexing feature 100 is an inward extended pin and the mating indexing feature 102 of the carburetor body 24 is an orifice or receptacle . when the block retainer 88 is utilized with the low and high - speed needle valves 26 , 28 a threaded fastener 104 secures the block retainer 88 to the carburetor body 24 . preferably , the threaded fastener is a screw or bolt , counter sunk into the block retainer 88 and threaded into the carburetor body 24 . referring to fig1 , yet another embodiment of the retainer assembly 20 ′ is shown wherein either the low or high - speed needle valve 26 , 28 is a fuel needle valve 106 and the remaining valve is eliminated and replaced with a dummy needle valve or shaft 108 which projects rigidly outward from the carburetor body 24 ′. the retainer 22 engages the fuel - air mixture needle valve 106 and the shaft 108 as it does with the low and high - speed needle valves 26 , 28 shown in fig1 . when utilizing the block retainer 88 embodiment of the retainer 22 , the shaft 108 is press fitted into the pilot hole 98 . this press fit eliminates the need for the threaded fastener 104 . the preferable material for the block retainer 88 is plastic . while the forms of the invention herein disclosed constitute presently preferred embodiments , many others are possible . it is not intended herein to mention all the possible equivalent forms or ramifications of the invention . it is understood that terms used herein are merely descriptive , rather than limiting , and that various changes may be made without departing from the spirit or scope of the invention .