OPEN IMPULSION VOLTAGE MACHINE DESCRIPTION OF THE INVENTION The present invention relates to open impulse scroll machines. More particularly, the present invention relates to scroll compressors that are driven externally and that incorporate a unique two-speed drive system for the open-drive volute machine. Scroll-type machines are becoming more and more popular for use as compressors in refrigeration applications as well as air conditioning due mainly to their extremely efficient operating capacity. Generally, these machines incorporate volute members having a pair of intermeshing coiled windings, one of which is orbited relative to the other to define one or more moving chambers that progressively decrease in size as they travel from an outer suction port towards a central discharge port. A certain type of power unit is provided which operates to drive the orbiting scroll member through a suitable drive shaft. The lower or lower portion of the housing containing the volute members typically contains a sump for lubrication of the various components of the compressor. Scroll machines can be separated into two categories based on the power unit that drives the volute member. The first category are volute machines having the power unit located within the housing together with the volute members. The housing containing the power unit and volute members can be opened to the environment or can be sealed to provide a hermetic scroll machine where the housing also contains working fluid from the scroll machine. The second category of volute machines are volute machines having the power unit separate from the housing containing the volute members. These machines are called open-drive volute machines and the housing containing the volute members is normally sealed from the environment so that the housing also contains the working fluid of the volute machine. The power unit for these open impulse scroll machines can be provided by a transmission belt and a pulley system, a gear transmission system, a direct transmission system or any other type of transmission system. The previous categories of volute machines can each be further subdivided into two additional categories of whether volute members are placed vertically which is more common with hermetic compressors or if scroll members are placed horizontally which is more common with the type of open transmission of scroll machines. Scrolling machines placed vertically and horizontally perform satisfactorily in their respective market. Typically, the power unit for these scroll machines is a more expensive single speed or variable speed transmission system. Several applications for volute machines can benefit if a volute machine has a low speed capacity and a high speed capacity. These two-speed scroll machines can be produced at a significantly lower cost than variable speed scroll machines and thus economically satisfy the market for applications that can benefit from a volute machine having a low capacity and capacity high speed. The present invention discloses a unique two-speed drive system for an open-drive horizontal volute machine that operates to operate the scroll machine at a low speed capacity when the speed machine's demand is low and a speed capacity high when the demand of the scroll machine is high. A unique planetary gear system is placed between the power unit and the transmission shaft of the volute machine to provide the two-speed capability. Other advantages and objects of the present invention will become apparent to those skilled in the art from the subsequent detailed description, attached claims and drawings. BRIEF DESCRIPTION OF THE DRAWINGS In the drawings which illustrate the best mode currently contemplated to carry out the present invention. Figure 1 is a vertical cross-section of a horizontal open-volute scroll machine incorporating the single transmission system in accordance with the present invention; and Figure 2 is a vertical cross section of an open horizontal scroll machine incorporating the single transmission system according to another embodiment of the present invention. Referring now to the drawings, there is shown in Figure 1 an open horizontal scroll compressor incorporating a unique two-speed transmission system in accordance with the present invention which is generally designated by reference numeral 10. The compressor 10 comprises a compressor body 12, a lid assembly 14, a main support housing 16, and a sump assembly 18, a lower support assembly 20, an orbiting volute member 22, a scroll member 24 not orbiter and a two-speed transmission system 26. The compressor body 12 is generally a cup-shaped member, preferably made of aluminum defining an internal cavity 28 within which the main support housing 16 is located, an internal hole 30 to coincide with the drain assembly 18 and the lower support assembly 20 and a suction inlet 32 to match the refrigeration circuit associated with the compressor 10. The compressor body 12, the lid assembly 14 and the lower support assembly 20 define a chamber 34 sealed within from which scroll members 22 and 24 are arranged. The lid assembly 14 comprises an adapter plate 36, a partition 38, a lid 40, a discharge fitting 42 and a temperature probe 44. The adapter plate 36 is secured to the compressor body 12 using a plurality of bolts 46. The division 38 is welded on its periphery to the adapter plate 36 at the same point that the cover 40 is welded to the division 38. The division 38 separates the chamber 34 in a suction chamber 48 and a discharge chamber 50. The discharge fitting 42 extends through the cover 40 and provides a discharge gas outlet from the discharge chamber 50 to the refrigeration circuit associated with the compressor 10. The temperature probe 44 extends through the cover 40. and division 38 so that it is located within a discharge recess 52 located within non-orbiting volute member 24. A dynamic discharge valve assembly 54 is located within the discharge recess 52 and is retained within the recess 52 by a nut received threadably within the recess 52. The main support housing 16 snaps into the cavity 28 of the body 12 of compressor and rests against a support 56 formed by the cavity 28. The surface of the main support housing 16 opposite the support 56 is provided with a flat thrust support surface 58 against which is located the orbiting scroll member 22 having a normal spiral or winding blade 60. Projecting opposite to the winding 60 is a cylindrical hub 62 having a plain bearing in which a drive bushing 66 is rotatably deposited. An Oldham coupling 70 is also provided positioned between the orbiting volute member 22 and the support housing 16. Coupling 70 Oldham engages the orbiting volute member 22 and non-orbiting volute member 24 to prevent rotational movement of the orbiting volute member 22. The Oldham coupling 70 is preferably of the type described in the assignee US Pat. No. 5,320,506, the disclosure of which is incorporated herein by reference. The non-orbiting volute member 24 is also provided with a winding 72 placed in mesh engagement with the winding 60 of the orbiting volute member 22. The non-orbiting volute member 24 has a centrally disposed passage communicating with the discharge recess 52 through the discharge valve assembly 54 which in turn is in communication with the chamber 50 of discharge defined by the lid 50 and the partition 38. An annular recess 76 is also formed in the non-orbiting volute member 24 within which a seal assembly 78 is disposed. The recesses 52 and 76 and the seal assembly 78 cooperate to define axial pressure that deflects the chambers receiving the pressurized fluid which is compressed by the windings 60 and 72 to exert an axial deflection force on the non-orbiting scroll member 24 for with this, the tips of the respective windings 60 and 72 in sealing engagement with the opposite end plate surfaces. The seal assembly 78 of preference is of the type described in greater detail in US Patent No. 5, 156,539, the description of which is incorporated herein by reference. The non-orbiting volute member 24 is designed to be mounted to the support housing 16 in a suitable manner as described in US Patent No. 4,877,382 or US Patent No. 5,102,316 both of which are incorporated herein by reference . A steel transmission shaft or crankshaft 80 having an eccentric journal at one end thereof is rotatably articulated in a sleeve bearing 84 in the main bearing housing 16 and a roller bearing 86 in the lower support assembly 20. The stump is disposed impenetrably within the inner bore of the transmission bushing 66. The stump has a flat surface on which a flat surface (not shown) formed in a portion of the bore of the transmission bushing 66 engages to provide a radially compliant transmission arrangement, as shown in the aforementioned US Pat. of the assignee 4,877,382. The crankshaft 80 includes an axially extending orifice that intersects with a radial inlet orifice and a radial outlet orifice. The end of the crankshaft 80 opposite the die extends through the lower support assembly 20 and is adapted to be connected to the two-speed drive system 26 which is being used to drive the crankshaft 80. The sump assembly 18 is disposed within of the chamber 34 in concentric relation with the transmission shaft 80. The sump assembly 18 comprises a housing, a pump body, a drive member and a plurality of vanes. The housing is secured to the compressor body 12 using a plurality of bolts. The housing defines an oil inlet passage and an oil outlet passage. The pump body is secured to the housing using a plurality of bolts and in this way the pump body is stationary. The pump body defines a pumping chamber within which the plurality of vanes is located. The drive member is driven urgently to the drive shaft 80 so that rotation of the drive shaft 80 causes rotation of the drive member. The rotation of the transmission shaft 80 causes the rotation of the drive member which in turn causes the rotation of the plurality of vanes in the pumping chamber and the pumping of oil between the inlet passage which is in communication with a supply passage extending through the compressor body 12 and in communication with a sump 102 located within the chamber 34 sealed through a filter. The outlet passage is in communication with a supply passage that extends through the compressor body 12 and is in communication with a filter chamber 106 formed by the compressor body 12. An oil filter 108 is disposed within the chamber 106 and the chamber 106 is closed by a filter cover 110 which is secured to the compressor body 12 using a plurality of bolts. The oil filter 108 is located between the supply passage and a return passage returning to the sump 102. A spring 112 biases the oil filter 108 away from the filter cover 110 to ensure oil flows through the filter 108 before entering the return passage. The return passage is a stepped diameter passage which restricts the flow of oil to increase the oil pressure thereby providing the oil to the moving components of the compressor 10. The lower support assembly 20 comprises the roller bearing 86 and a 114 pressure ring. The roller bearing 86 is disposed between the drive shaft 80 and the housing of the sump assembly 18 and the pressure ring 114 places the bearing 86 against a support in the drive shaft 80. A bearing spacer and a Belville spring are placed between the two-speed drive system 26 and the outer race of the bearing 86 to properly secure the bearing 86. The two-speed drive system 26 comprises a planetary gear set 120., a clutch assembly 122 and an end cap assembly 124. The planetary gear assembly 120 comprises a planetary gear 130, a plurality of planetary gears 132 and a ring gear 134. The planetary gear 130 is attached to the transmission shaft 80. The plurality of planetary gears 132 mesh with the planetary gear 130 and are joined to the input shaft 136. The input shaft 136 extends through the end cap assembly 124 and provides the drive input to drive the two speed drive system 126 and thus the drive shaft 80. A one-way clutch 138 is disposed between the input shaft 136 and the planetary gear 130. The one-way clutch 138 allows the planetary gear 130 to rotate faster than the input shaft 136 but will provide the driving power from the input shaft 136 to the planetary gear 130 when necessary as detailed in the following. The ring gear 134 is in engagement with the plurality of planetary gears 132 and is rotatably disposed within the compressor body 12. The clutch assembly 122 comprises a clutch housing 140, a piston 142, a biasing member in the spring 144 and a clutch plate 146. The clutch housing 140 is attached to the compressor body 12 and thus rotation with respect to the compressor body 12 is prevented. The piston 142 and the compressor body 12 define a chamber 148. An inlet port 150 extends through the compressor body 12 to provide communication with the chamber 148. A fluid pressure line 152 extends between the port 150 of the compressor body. entrance and the discharge chamber 50. A solenoid valve 154 controls the flow of pressurized fluid through the fluid pressure line 152. The spring 144 deflects the piston 142 to the right as shown in Figure 1 to engage the clutch assembly 122. In its coupled position the clutch assembly 122 prohibits the rotation of the ring gear 134. With the lock ring gear 134, the power of the input shaft 136 is provided to the planetary gears 132 that provide an increase in speed for the planetary gear 130. The increase in speed for the planetary gear 130 is facilitated by the incorporation of the one-way clutch 138 that allows the faster rotation of the planetary gear 130. The planetary gear 130 is attached to the drive shaft 80 to drive the compressor 10. In this way, when the clutch assembly 122 engages, the planetary gear assembly 120 increases the speed between the input shaft 136 and the shaft 80 of the planetary gear. transmission to provide a high-speed capability for the two-speed drive system 26. The amount of speed increase between the input shaft 136 and the transmission shaft 80 will be determined by the diameter of the ring gear 134 and the diameter of the planetary gear 130. When the low speed operation for the two speed drive system 26 of the compressor 10 is desired, the solenoid valve 154 is activated to position the chamber 148 in communication with the discharge chamber 50 through the pressure line 152 and the Louvre 150 inlet. The pressurized fluid within the chamber 148 reacts against the piston 142 to move the piston 142 to the left as shown in Figure 1 to release the ring gear 134 for rotation. Typically, in a planetary gear train, the input power drives a member, the second member is driven to provide the output and the third member is fixed. If the third member is not fixed, the power is not distributed. The one-way clutch 138 is incorporated to provide low speed rotation of the two-speed drive system 26. When the solenoid valve 154 is energized and the chamber 148 is pressurized, the clutch assembly 122 releases the ring gear 134 for rotation. The planetary gear 130 is no longer energized by the planetary gears 132 and thus the planetary gear 130 will begin to decelerate. The planetary gear 130 will lower the speed until the one-way clutch 138 is engaged in this way by equalizing the speed between the input shaft 136 and the planetary gear 130 resulting in a one-to-one or low-speed rotation for the system. of two speeds. When it is desired to return to the high-speed rotation the two-speed drive system 26, the pressurized fluid within the chamber 148 is released into the chamber 34 sealed by the solenoid valve 154. The release of the pressurized fluid from the chamber 148 causes the springs 144 to again move the piston 142 to the right as shown in Figure 1 by engaging the clutch assembly 122 to place the two speed drive system 26 in high speed condition. . The sealed chamber 34 is closed by an end cover assembly 160 comprising a cover plate 162 and a support cover 164. The support cover 164 defines an internal chamber 166 having a plurality of radially extending and circumferentially spaced ridges that place a spacer 168 and a plurality of seals 170 between the input shaft 136 and the support cover 164. The input shaft 136 extends through the support cover 164 and is adapted for connection to an external power supply by methods well known in the art. Thus, the incorporation of the planetary gear assembly 120 and the clutch assembly 122 provide a simple and relatively inexpensive method for providing a two speed capability for the compressor 10. Referring now to Figure 2, a horizontal scroll compressor open which incorporates a unique two-speed drive system according to another embodiment of the present invention is illustrated and is generally designated by the reference number 210. The compressor 210 is the same as the compressor 10 except that the clutch assembly 122 has been replaced by the clutch assembly or solenoid valve assembly 222. The solenoid valve assembly 222 comprises a solenoid core 224, a solenoid coil 226 and a clutch plate 146. At low input speeds or when high compressor capacity demand requirements are present, the solenoid coil 226 is energized, thereby attracting the clutch plate 146 and fixing it to the solenoid core 224. In this fixed position, rotation of the ring gear 134 is prohibited. With the ring gear 134 fixed, the power of the input shaft 136 is provided to the planetary gears 132 which result in an increase in the speed for the planetary gear 130. The increase in speed for the planetary gear 130 is facilitated by the incorporation of the one-way clutch 138 that allows the faster rotation of the planetary gear 130. The planetary gear 130 is attached to the drive shaft 80 to drive the compressor 210. Thus, when the solenoid coil 226 is energized, the planetary gear assembly 120 increases the speed between the input shaft 136 and the shaft 80 of transmission to provide a high-speed capability for the two-speed drive system 26. The amount of speed increase between the input shaft 136 and the drive shaft 80 will be determined by the diameter of the ring gear 134 and the diameter of the planetary gear 130. At higher input speeds or when lower compressor capacity demand requirements are present, the solenoid coil 226 is energized which results in the de-clutching of the solenoid core 224 of the clutch plate 146 allowing rotation of the gear 134 of ring. Typically, in a planetary gear train, the input power drives a member, the second member is provided at the output and the third member is fixed. If the third member is not fixed, no power is distributed. The one-way clutch 138 is incorporated to provide low speed operation of the two-speed drive system 26. When the solenoid coil 226 is deenergized, the clutch assembly or solenoid valve 222 releases the ring gear 134 for rotation. The planetary gear 130 is no longer energized by the planetary gears 132 and thus the planetary gear 130 will start to slow down. The planetary gear 130 will lower its speed until the one-way clutch 138 is engaged, thereby equalizing the speed between the input shaft 136 and the planetary gear 130 resulting in a one-to-one or low-speed rotation for the 26 two-speed drive system. When it is desired to return to the high-speed operation of the two-speed drive system 26, the solenoid coil 226 can be energized again to couple the clutch plate 146 with the solenoid core 224 to position the two-speed drive system 26 in its high speed condition. Thus, the incorporation of the planetary gear assembly 120 and the solenoid valve assembly 222 provide a simple and relatively inexpensive method to provide a two speed capability for the compressor 210. The two speed drive system 26 with the assembly The clutch 122 or the solenoid valve assembly 222 can be used to drive any other type of positive displacement compressor with open drive. Although the two-speed drive system 26 with the clutch assembly 122 in the solenoid valve assembly 222 has been illustrated as being located within the sealed chamber 34, it is within the scope of the present invention to mount the drive system 26 two speed external to the compressor or the sealing chamber 34. When mounted externally to the compressor or to the sealed chamber 34, the two speed drive system 26 can be packaged together with a drive pulley and transmission pulley clutch. Although the two-speed drive system 26 is illustrated in use with a horizontal compressor, it can be integrated into a vertical hermetic compressor, if desired. Preferably, in the vertical hermetic compressor, the two-speed drive system 26 is placed between the motor rotor and the lower bearing. The planetary gear is attached to the crankshaft, the motor rotor has bearings so that it can rotate in the compressor shaft with the speed differential that is between the crankshaft and the rotor. The rotor can then drive the planetary gear housing assembly. With the implementation of the mechanism described above, the two-speed operation can be achieved using a single-speed motor and due to the increased or high-speed operation, the largest compressor capacity can be achieved in a smaller compressor frame or diameter of armor. Although the above-described description describes the preferred embodiment of the present invention, it should be understood that the present invention is susceptible to modification, variation and alteration without departing from the scope and favorable meaning of the appended claims.