Abstract:
An energy-saving, downsized gas supply apparatus equipped with a vaporizer is provided, wherein the gas supply apparatus is capable of stably and easily performing highly accurate gas flow rate control without requiring rigorous temperature control on the vaporizer side. The present invention pertains to a gas supply apparatus equipped with a vaporizer that includes (a) a liquid receiving tank; (b) a vaporizer that vaporizes liquid; (c) a high-temperature type pressure type flow rate control device that adjusts a flow rate of a vaporized gas; and (d) heating devices that heat the vaporizer, the high-temperature type pressure type flow rate control device, and desired portions of pipe passages connected to the vaporizer and the high-temperature type pressure type flow rate control device.

Description:
This is a National Phase Application in the United States of International Patent Application No. PCT/JP2009/000643 filed Feb. 17, 2009, which claims priority on Japanese Patent Application No. 2008-094640, filed Apr. 1, 2008. The entire disclosures of the above patent applications are hereby incorporated by reference. 
     FIELD OF THE INVENTION 
     The present invention relates to improvements in a gas supply apparatus equipped with a vaporizer used for semiconductor manufacturing devices, chemical industrial facilities, medical industrial facilities, and the like, and relates to a gas supply apparatus equipped with a vaporizer having a simple structure, which makes possible energy saving and downsizing of the unit. The unit is capable of easily performing temperature management and flow rate control by combining a vaporizer and a high-temperature type pressure type flow rate control device to make use of the stable flow rate control characteristics of the pressure type flow rate control device. 
     BACKGROUND OF THE INVENTION 
     For semiconductor manufacturing facilities, many gas supply systems have been conventionally used in which various types of liquefied gases for semiconductor manufacturing are received into their tanks and are gasified by their vaporizers, and then are supplied to process chambers. For example,  FIG. 12  shows an example of a basic configuration of a gas supply apparatus composed of a vaporizer Va and a liquid type thermal mass flow rate control device LMFC. The gas supply apparatus is configured so that a liquefied gas LG, received in a liquefied gas receiving tank T, is fed to the vaporizer Va by use of the pressure of a gas Gp for pressurizing or by the use of a pump for feeding liquid (not shown), while controlling its flow rate by the liquid type thermal mass flow rate control device LMFC, in order to supply a vaporized gas G at a predetermined flow rate to a process chamber CH. In addition, reference character H is a heating region. 
     Meanwhile, because the liquid type thermal mass flow rate control device LMFC is used for the gas supply apparatus of  FIG. 12 , there is the problem that an error in a vaporized gas flow rate becomes inevitably large even when an error in flow rate control in a liquid state is small. This makes it difficult to accurately control gas flow rate. 
     Therefore, as shown in  FIG. 13 , a gas supply apparatus of a type in which a high-temperature type thermal mass flow rate control device HMFC is connected to the downstream side of the vaporizer Va has been developed to make an attempt to perform highly accurate mass flow rate control of a vaporized gas G. However, because the high-temperature type thermal mass flow rate control device HMFC has the characteristic that controlling flow rate is greatly changed according to fluctuation of a primary side flow rate and pressure, it is necessary to maintain a secondary side flow rate and pressure of the vaporizer Va at predetermined setting values by highly accurately performing temperature control on the side of the vaporizer Va in order to perform highly accurate flow rate control for the gas flow rate. Furthermore, it is necessary to set a temperature of its sensor portion to be higher than a temperature of its main line in the high-temperature type thermal mass flow rate control device HMFC, which may easily bring about decomposition and deposition of the liquid source (material). 
     On the other hand, in order to highly accurately maintain the secondary side of the vaporizer Va at a predetermined flow rate and pressure, it is necessary to highly accurately perform temperature control of the vaporizer Va as described above and, as a result, it is necessary to increase a heating volume and enlarge a heating region. Therefore, not only is the gas supply apparatus itself increased in size by necessity, but also various inconveniences are brought about in terms of energy saving, operating cost, and the like. 
     [Patent Document 1] Japanese Published Unexamined Patent Application No. H11-278987 
     [Patent Document 2] Japanese Published Unexamined Patent Application No. 2003-142473 
     [Patent Document 3] Japanese Published Unexamined Patent Application No. 2004-143591 
     [Patent Document 4] Japanese Published Unexamined Patent Application No. 2007-036265 
     Problems to be Solved by the Invention 
     The present invention has been constructed in order to solve the problems described above in a gas supply apparatus according to a combination of a conventional liquid type thermal mass flow rate control device LMFC and a vaporizer Va, or a combination of the vaporizer Va and a high-temperature type thermal mass flow rate control device as follows: (a) in the case where a liquid type thermal mass flow rate control device is used, even a small error in the amount of liquid leads to a great error in gas volume due to its expansion, which makes it impossible to perform accurate flow rate control of a liquefied gas G; and (b) in the case where a high-temperature type thermal mass flow rate control device HMFC is used, highly accurate temperature control of the vaporizer Va is required, which results in an increase in size of the gas supply apparatus or results in making the temperature control device complex. An object of the present invention is to provide a gas supply apparatus equipped with a vaporizer in which the vaporizer Va and a high-temperature type pressure type flow rate control device HFCS are combined in a manner that is capable of performing highly accurate flow rate control of a vaporized gas G with so-called “rough temperature” control and flow rate control, and a downsized gas supply apparatus without requiring specific highly accurate temperature control and flow rate control. 
     SUMMARY OF THE INVENTION 
     In order to achieve the object(s) of the invention, the invention, according to a first embodiment, has the basic configuration of a gas supply apparatus equipped with a vaporizer including: a liquid receiving tank; a vaporizer that vaporizes liquid pressure-fed from the liquid receiving tank; a high-temperature type pressure type flow rate control device that adjusts a flow rate of outflow gas from the vaporizer; and heating devices that heat the vaporizer, the high-temperature type pressure type flow rate control device, and desired portions of pipe passages connected to the vaporizer and the high-temperature type pressure type flow rate control device. 
     The invention, according to a second embodiment, is that in the invention according to the first embodiment, the liquid is any one of water (H 2 O), hydrogen fluoride (HF), tetraethoxysilane (TEOS), trimethylaluminum (TMA), or tetrakis(diethylamino)hafnium (TDEAH). 
     The invention according to a third embodiment is that, in the invention according to the first embodiment, a device main body of the high-temperature type pressure type flow rate control device is mounted on a vaporizing chamber of the vaporizer. 
     The invention according to a fourth embodiment further includes, in the invention according to the first embodiment, a liquid supply control device that adjusts an amount of liquid to be pressure-fed to the vaporizer from the liquid receiving tank so that the gas pressure on the upstream side of the high-temperature type pressure type flow rate control device reaches a predetermined setting pressure or higher. 
     The invention according to a fifth embodiment further includes, in the invention according to the first embodiment, a temperature control device that adjusts a heating temperature of the vaporizer so that the pressure on the upstream side of the high-temperature type pressure type flow rate control device reaches a predetermined setting pressure or higher. 
     The invention according to a sixth embodiment is that, in the invention according to the first embodiment, the vaporizer is composed of the vaporizing chamber provided with a desired internal space volume, a plurality of orifices for dampening pulsation, which are arranged with spaces between them inside the vaporizing chamber, and heaters installed on the outer side surfaces of the vaporizing chamber. 
     The invention according to a seventh embodiment is that, in the invention according to the first embodiment, a relief valve is provided in a pipe passage between the vaporizer and the high-temperature type pressure type flow rate control device, wherein the relief valve operates to relieve pressure when the gas pressure in the pipe passage reaches an approximately predetermined maximum allowable working pressure of the high-temperature type pressure type flow rate control device. 
     The invention according to an eighth embodiment is that in the invention according to the first embodiment, high-temperature type pressure type flow rate control is performed by the gas supply apparatus so as to heat the device main body of the high-temperature type pressure type flow rate control device to a temperature of 20° C. to 250° C. by a heater. 
     The invention according to a ninth embodiment is that, in the invention according to the first embodiment, a heating temperature of the vaporizer is set to 20° C. to 250° C. 
     The invention according to a tenth embodiment is that, in the invention according to the first embodiment, a buffer tank is disposed in the pipe passage between the vaporizer and the high-temperature type pressure type flow rate control device. 
     The invention according to an eleventh embodiment is that, in the invention according to the six embodiment, the vaporizer is configured so that the vaporizing chamber of the vaporizer is a metal vaporizing chamber and is provided with heat equalizing plates on its outer side surfaces, and is further equipped with insulating materials on its outer sides. 
     The invention according to a twelfth embodiment is that, in the invention according to the six embodiment, the vaporizing chamber of the vaporizer is equipped with a pool part for liquid content existing in the vaporizing chamber. 
     The invention according to a thirteenth embodiment is that, in the invention according to the six embodiment, the metal vaporizing chamber is formed into a metal cylindrical vaporizing chamber, and the orifice for dampening pulsation is formed into a discoid shape, and the two orifices for dampening pulsation are arranged in parallel with a space inside the vaporizing chamber. 
     The invention according to a fourteenth embodiment is that, in the invention according to the six embodiment, the inside of the vaporizing chamber is filled with a heating accelerator made of steel balls and porous metal plates. 
     The invention according to a fifteenth embodiment is that, in the invention according to the eighth embodiment, aluminum heat equalizing plates are firmly fixed to the device main body of the high-temperature type pressure type flow rate control device, and sheath heaters are arranged at the vicinities of a passage on the side of a gas inlet and a passage on the side of a gas outlet of the device main body, to maintain a temperature difference between portions contacting the gas at 6° C. or less. 
     The invention according to a sixteenth embodiment is that, in the invention according to the eighth embodiment or the ninth embodiment, a heater configured so that a sheath heater with a desired length is inserted and fixed into a heater insertion groove formed in the inner side surface of an aluminum thick plate installed on both side surfaces of the high-temperature type pressure type flow rate control device, or on both side surfaces and bottom surface of the vaporizer. 
     Effects of the Invention 
     In the present invention, because a flow rate of a gas vaporized by the vaporizer is controlled by the high-temperature type pressure type flow rate control device that has stable flow rate control characteristics, even when the conditions on the side of the vaporizer fluctuate to a certain degree, the fluctuation does not have a considerable effect on its flow rate measurement accuracy on the side of the flow rate control device. As a result, even when temperature control accuracy, or pressure control (liquid inflow control) accuracy, on the side of the vaporizer is somewhat low or fluctuated to a certain degree, its flow rate control accuracy on the side of the gas does not deteriorate in any case, which makes it possible to stably perform highly accurate gas flow rate control. 
     Furthermore, because the internal space of the vaporizing chamber of the vaporizer is partitioned into a plurality of compartments provided with orifices for dampening pulsation, and because the pool part for liquid content remaining inside the vaporizing chamber is provided to discharge the liquid content in the pool part to the outside, pressure fluctuation in the vaporizing chamber due to the remaining liquid content is significantly reduced. 
     Moreover, the pressure of the supplying gas to the flow rate control device is stabilized by providing a buffer tank between the vaporizer and the high-temperature type pressure type flow rate control device. This makes it possible to perform further highly accurate gas flow rate control. 
     Because the vaporizing chamber is heated by the heaters and the heat equalizing plates are installed on the outer side surfaces of the vaporizing chamber, the vaporizing chamber is uniformly heated. This makes it possible to perform more stable vaporization of the liquid content. 
     Because the high-temperature type pressure type flow rate control device is set to 50° C. to 200° C. by cartridge heaters, and the aluminum heat equalizing plates are attached to the main body of the high-temperature type pressure type flow rate control device, and the auxiliary sheath heaters are installed in the passage on the side of the gas inlet and are installed on the passage on the side of the gas outlet, it is possible to maintain a temperature difference between portions contacting the gas at 6° C. or less. It is also possible to completely prevent the generation of a liquid content in the flow rate control device main body. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         FIG. 1  is a basic block diagram schematically showing a gas supply apparatus A including a vaporizer according to the present invention. 
         FIG. 2  is a cross-sectional schematic diagram of a vaporizer  1  used in the present invention. 
         FIG. 3  is a basic block diagram schematically showing a high-temperature type pressure type flow rate control device  2  used in the present invention. 
         FIG. 4  is a cross-sectional schematic diagram of a control device main body portion of the high-temperature type pressure type flow rate control device  2  used in the present invention. 
         FIG. 5  shows a schematic perspective view of a heater  13  according to an embodiment of the invention. 
         FIG. 6  is a partially cutaway schematic perspective view of a vaporizing chamber  3  according to another embodiment of the present invention. 
         FIG. 6   a  is a partially cutaway schematic perspective view of a vaporizing chamber  3  showing steel balls and porous metal plates in accordance with the present invention. 
         FIG. 7  is a schematic perspective view of a gas supply apparatus A, including a vaporizer, according to an embodiment of the present invention. 
         FIG. 8  is an explanatory diagram of a vaporization experiment by a vaporizer  1  according to the present invention. 
         FIG. 9  is a graph showing a relationship between elapsed times and pressures of respective parts of the gas supply apparatus in Experiment 1. 
         FIG. 10  is a graph showing a relationship between elapsed times and flow rates of a high-temperature type pressure type flow rate control device in Experiment 1. 
         FIG. 11  is a graph showing a relationship between elapsed times, pressures of the respective parts of the gas supply apparatus, and flow rates of a pressure type flow rate control device in Experiment 2. 
         FIG. 12  is an explanatory diagram showing an example of a gas supply apparatus including a conventional vaporizer. 
         FIG. 13  is a diagram showing another example of a gas supply apparatus including a conventional vaporizer. 
     
    
    
     DESCRIPTION OF SYMBOLS 
     A: gas supply apparatus equipped with a vaporizer, T: liquid receiving tank, LG: liquid, G: gas, V 1 : liquid supply rate control valve, V 2  to V 7 : on-off valves, Q: liquid supply rate control device, M: heating temperature control device, L: relief valve, Gp: gas for pressurizing the liquid receiving tank, To: heater temperature detector, P 0  to P 1 : pressure detectors, T 1 : temperature detector,  1 : vaporizer,  2 : high-temperature type pressure type flow rate control device,  3 : vaporizing chamber,  3   a ,  3   b ,  3   c : block bodies,  3   d : liquid inlet,  3   e : gas outlet,  3   f ,  3   g : heating accelerators,  4 : orifice for dampening pulsation,  4   a : orifice hole,  5 : liquid pool part,  6  to  8 : heating devices,  9 : control valve,  9   a : driving section,  9   b : diaphragm valve body,  10 : orifice,  11 : buffer tank,  12 : heat equalizing plate,  13 : heater,  13   a : aluminum plate,  13   b : heater insertion groove,  13   c : coil heater,  14 : heat insulating material,  15 : arithmetic control device,  15   a : flow rate arithmetic section,  15   b : comparison section,  15   c : amplifier/AD converter,  15   d : setting input section,  16 : control device main body,  16   a : gas outlet,  17 : cartridge heater,  18 : auxiliary sheath heater,  19 : pipe passage,  20 : process chamber,  21 : vacuum pump,  22 : orifice,  23 : pipe passage. 
     DETAILED DESCRIPTION OF THE INVENTION 
     Best Mode for Carrying Out the Invention 
     Hereinafter, a nonlimiting embodiment of the present invention will be described with reference to the accompanying drawings. In the figures, like character references are employed to designate like parts.  FIG. 1  is a block diagram showing a basic configuration of a gas supply apparatus A including a vaporizer according to the present invention. In  FIG. 1 , reference character T denotes a liquid receiving tank, reference character Q denotes a liquid supply rate control device, reference character M denotes a heating temperature control device, reference character V 1  denotes a liquid supply rate control valve, reference character L denotes a relief valve, reference character Gp denotes a gas for pressurizing the liquid receiving tank, reference character To denotes a heater temperature detector, reference characters V 2  to V 7  denote on-off valves, reference characters P 0  and P 1  denote pressure detectors, reference character T 1  denotes a temperature detector, reference numeral  1  denotes a vaporizer, reference numeral  2  denotes a high-temperature type pressure type flow rate control device, reference numeral  3  denotes a vaporizing chamber, reference numeral  4  denotes an orifice for dampening pulsation, reference numeral  5  denotes a liquid pool part, reference numerals  6  to  8  denote heating devices, reference numeral  9  denotes a control valve, reference numeral  10  denotes an orifice, reference numeral  11  denotes a buffer tank, reference numeral  19  denotes a pipe passage, and reference numeral  20  denotes a process chamber. In addition, the liquid pool part  5  and the buffer tank  11  may be eliminated in accordance with some embodiments of the invention. 
     The gas supply apparatus A equipped with the vaporizer of the present invention (hereinafter abbreviated to the “gas supply apparatus”) is composed of the liquid receiving tank T, the liquid supply rate control device Q, the vaporizer  1 , the high-temperature type pressure type flow rate control device  2  (hereinafter abbreviated to the “pressure type flow rate control device”), the heating devices  6 ,  7 , and  8 , and the like. The vaporizer  1 , the pressure type flow rate control device  2 , and the combined structure of both compose a substantial part of the present invention. 
       FIG. 2  is a cross-sectional schematic diagram of the vaporizer  1  used for the present invention. The vaporizer  1  is composed of a case  3  (forming the vaporizing chamber), whose planar shape is quadrangular, and the two orifices for dampening pulsation  4 , which partition the inside of the case  3  into three compartments, the liquid pool part  5 , a drainage mechanism from the liquid pool part  5 , aluminum heat equalizing plates  12  that are firmly fixed to both top and bottom surfaces and the front and rear side surfaces (not shown) of the vaporizing chamber  3 , heaters  13  installed on the outer surfaces of the heat equalizing plates  12 , with heat insulating materials  14  covering the outsides of the heaters  13 . The vaporizer  1  also includes the pressure detector P 0 , and the like. 
     The vaporizing chamber  3  is formed of stainless steel made into a case having an appropriate volume with an internal volume of 10 cm 3  or more, and a value of the internal volume is appropriately determined according to the type of liquid LG and a required gas flow rate. As will be described later, in the case where the liquid LG is purified water and the required gas flow rate is 100 Standard Cubic Centimeters per Minute (SCCM), the internal volume of the vaporizing chamber  3  is set to be approximately 18 cm 3 . Furthermore, the orifice  4  for dampening pulsation, as well, is formed of stainless steel, and an inner diameter of its orifice hole  4   a  is appropriately specified according to the type of liquid LG or to the amount of liquid to be vaporized. In the case where the liquid LG is water and the required gas flow rate is 100 SCCM, the respective hole diameters of the two orifices  4  are set to 0.2 mmφ. Moreover, as shown in  FIG. 2 , the internal space of the vaporizing chamber  3  is partitioned into three compartments. However, the partitioning number for partitioning the chamber  3  into compartments is specified as 2 to 5 according to an allowable fluctuation width of inner pressure P 0  on the side of the outlet of the chamber  3 . In other words, chamber  3  may be partitioned into two to five compartments. 
     The vaporizer  1  is heated to approximately 50° C. to 300° C. by the heating device  6  composed of the heaters  13 , the aluminum heat equalizing plates  12 , and the like, and the liquid is made into a gas G at a temperature of 20° C. to 250° C. so it may flow out toward the pressure type flow rate control device  2 . In the vaporizer  1  of  FIG. 2 , the vaporizing chamber  3  is formed into a box shape. However, the vaporizing chamber  3  may be formed into a cylindrical shape, and the orifice  4  for dampening pulsation may be formed into a discoid shape, and a plurality of the orifices  4  are arranged in parallel with each other, and are welded so as to be fixed to the inner wall surface of the vaporizing chamber  3 . 
     In the embodiment of  FIG. 2 , the inside of the vaporizing chamber  3  is made as a space portion other than the orifices  4 , which form additional space portions. Meanwhile, in order to accelerate heating of liquid (i.e., liquefied gas) LG, and to maintain a temperature of a vaporized gas, a heating accelerator (not shown) composed of small diameter steel balls and a laminated body of porous metal plates may be supplied by desired amounts to the inside of the vaporizing chamber  3  in order to fill up the internal space of the vaporizing chamber  3 . Furthermore, the liquid pool part  5  is provided on the side of the outlet of the vaporizing chamber  3  as shown in  FIG. 2 . Meanwhile, the liquid pool part  5  and the drainage mechanism may be omitted in accordance with some embodiments of the invention. 
       FIG. 3  is a basic block diagram of the high-temperature type pressure type flow rate control device  2  used in accordance with the present invention. In  FIG. 3 , reference numeral  9  denotes a control valve, reference numeral  9   a  denotes a driving section, reference numeral  10  denotes an orifice, and reference numeral  15  denotes an arithmetic control device. Detected values of the pressure detector P 1  and the temperature detector T 1  are input to a flow rate arithmetic section  15   a  through an amplifier/AD converter  15   c , and a gas flow rate Qc passed through the orifice  10  is computed as Qc=KP 1 , wherein K is a constant. Thereafter, when a setting flow rate value Qs outputted from a setting input section  15   d  and the computed flow rate value Qc are compared in a comparison section  15   b , and a differential signal Qy between both is input from the comparison section  15   b  to the driving section  9   a  of the control valve  9 , the control valve  9  is opened and closed in a direction that causes the differential signal Qy to become zero. 
     The pressure type flow rate control device  2  is based on the standard notion that it is possible to compute a gas flow rate Q passing through an orifice  10  as Q=KP 1  (K is a constant, and P 1  is pressure on the upstream side of the orifice) in the case of a fluid flow in a so-called “critical state” in which a gas flow velocity passing through the orifice  10  is faster than or equal to the sound velocity (i.e., the velocity of sound). Accordingly, its responsiveness for flow rate control is extremely high and stable, and the pressure type flow rate control device  2  has excellent control responsiveness and a high control accuracy, which are far superior to those of a thermal mass flow rate control device. Because a pressure type flow rate control device itself is publicly known from Japanese Published Unexamined Patent Application No. H8-338546 and other applications, a detailed description thereof will be omitted here. 
     In addition, the control valve  9 , the orifice  10 , the pressure detector P 1 , the temperature detector T 1 , the arithmetic control device  15 , and the like composing the high-temperature type pressure type flow rate control device  2  are, as shown in the schematic view of  FIG. 4 , all integrally assembled with a stainless steel device main body  16 . That is to say that cartridge heaters  17  are inserted so as to be fixed to the device main body  16  (which may simply be referred to as “body”), and the device main body  16  and the portion of a diaphragm valve element  9   b  of the control valve  9  are heated to approximately 50° C. to 300° C. by the cartridge heaters  17 . 
     Furthermore, auxiliary sheath heaters  18  are installed onto portions of the fluid passages formed in the device main body  16 , and the vicinities of the inlet fluid passage and the outlet fluid passage are also heated by the auxiliary sheath heaters  18 . As a result, in the case where a liquid LG is purified water (H 2 O), hydrogen fluoride (HF), or tetraethoxysilane (TEOS.Si(OC 2 H 5 ) 4 ), the temperature of the passing gas G is maintained within a range of at least 20° C. to 250° C., then adhesion of liquid onto the diaphragm valve element  9   b  of the control valve  9  is completely prevented, and a difference between the gas temperatures in both fluid passages is maintained at approximately 6° C. or less. In addition, in accordance with the present invention, as liquid LG for the source of supply, there are trimethylindium (TMI.(CH 3 ) 3 In), dimethylzinc (DMZ.(CH 3 ) 2 Zn), diethylzinc (DEZ.(C 2 H 5 ) 2 Zn), trimethylgallium (TMG.(CH 3 ) 3 Ga), triethylgallium (TEG.(C 2 H 5 ) 3 Ga), trimethylaluminum (TMA.(CH 3 ) 3 Al), triethylaluminum (TEA.(C 2 H 5 ) 3 Al), tetrakis(diethylamino)hafnium (TDEAH.Hf[N(C 2 H 5 ) 2 ] 4 ), tetrakis(ethylmethylamino)hafnium (Hf[N(CH 3 )(C 2 H 5 )] 4 ), tetrakis(ethylmethylamino)zirconium (TEMAZ.(Zr[N(CH 3 )(C 2 H 5 )] 4 ), tantalum penta-ethoxide (TAETO.Ta(C 2 H 5 ) 5 ), tri(dimethylamino)silane (TDMAS.SiH[N(CH 3 ) 2 ] 3 , trimethylsilane (3MS.(CH 3 ) 3 SiH), tetramethylsilane (4MS.(CH 3 ) 4 Si), bis(tert-butylamino)silane (BTBAS.H 2 Si[NH(t-C 4 H 9 )] 2 ), triethyl phosphate (TEPO.O(C 2 H 5 O) 3 ), triethyl borate (TEB.B(OC 2 H 5 ) 3 ), titanium tetrachloride (TiCl 4 ), and the like, which are suitable to use. 
     Moreover, the relatively thick aluminum heat equalizing plates  12  are firmly fixed to the top surface side and both front and rear side surfaces (not shown) of the apparatus main body  16 , and temperatures of the respective parts of the control device main body  16  are made uniform by the heat equalizing plates  12 . As shown in  FIG. 4 , the heating device  7  of the pressure type flow rate control device  2  is composed of the cartridge heaters  17  and the auxiliary sheath heaters  18 . In addition, it is a matter of course that heaters to be used in the present invention may be of any type and in any mode of usage. 
       FIG. 5  is a schematic perspective view of the heater  13  used in accordance with the present invention (See  FIG. 2  as well). The heater  13  is configured so that a heater insertion groove  13   b  is provided in the inner side surface of a quadrangular aluminum plate  13  provided with a thickness of 4 to 8 mm, and a linear coil heater  13   c  is inserted and fixed into the heater insertion groove  13   b.    
       FIG. 6  is a partially cutaway schematic perspective view of the vaporizer according to another embodiment of the present invention. The vaporizing chamber  3  is formed so that three block bodies  3   a ,  3   b , and  3   c  are assembled in an airtight manner, and the liquid LG fed into the vaporizer from a liquid inlet  3   d  is vaporized, while passing of the liquid LG through the orifice holes  4   a  of the orifices  4  to flow out of a gas outlet  3   e . Reference numerals  3   f  and  3   g  denote heating accelerators composed of small diameter steel balls and a laminated body of porous metal plates. 
       FIG. 6   a  is a partially cutaway schematic perspective view of a vaporizing chamber  3  showing the heating accelerator  3   f  made up of steel balls  3   h . The heating accelerator  3   g  is shown made up of porous plates  3   i . Located between the heating accelerators  3   f  and  3   g  is heat accelerator  3   j  made up of porous plates  3   k.    
       FIG. 7  is a schematic perspective view showing an embodiment of the gas supply apparatus A equipped with the vaporizer according to the present invention. The gas supply apparatus A is configured so that the high-temperature type pressure type flow rate control device  2  is mounted on the vaporizer  1  as shown in  FIG. 6 . Moreover, the plate-like heaters  13  shown in  FIG. 5  are installed on both side surfaces and bottom surface of the vaporizer  1  and on the device main body  16  of the high-temperature type pressure type flow rate control device  2  so as to heat these structures. Reference numeral  16   a  in  FIG. 7  denotes a gas outlet. However, an illustration of the outermost heat insulating material is omitted. The outermost heat insulating material  14  is shown in  FIG. 2  and may be applied to the embodiment of  FIG. 7 . 
     Next, a general description of the operation in the present invention will be described. Referring to  FIG. 1 , a supply rate of the liquid LG from the inside of the liquid receiving tank T is controlled by adjusting the inner pressure in the tank T and the opening degree of the liquid supply rate control valve V 1  via the liquid supply rate control device Q, and a supply rate of the liquid LG is controlled such that the gas pressure on the upstream side of the high-temperature type pressure type flow rate control device  2  is set to a predetermined pressure value or greater by a signal from the pressure detector P 0  disposed on the outlet side of the vaporizer  1 . In the same way, input to the heaters  13  of the heating device  6  and adjustment of an opening degree of the liquid supply rate control valve V 1  are performed via the heating temperature control device M by a signal from a heating temperature detector To of the vaporizer  1 , and the gas pressure on the upstream side of the high-temperature type pressure type flow rate control device  2  is controlled so as to be set to a desired flow rate and pressure value or greater by the liquid supply rate control device Q and the heating temperature control device M. 
     The relief valve L is provided in the pipe passage through which the vaporizer  1  and the high-temperature type pressure type flow rate control device  2  communicate with each other. Thus, in the case wherein gas pressure on the outlet side of the vaporizer  1  rises abnormally, the gas G is discharged to the outside to relieve gas pressure. 
     Furthermore, the buffer tank  11  shown in  FIG. 1  stores a predetermined volume of the gas G to prevent a significant fluctuation in flow rate (pressure) of the gas G flowing into the pressure type flow rate control device  2 . Because the pressure type flow rate control device  2  is excellent in responsiveness as described above, even when there is a certain fluctuation in flow rate (pressure) of the outflow gas G from the vaporizer  1 , no trouble is brought about in the flow rate control itself. Therefore, the volume of the buffer tank  11  may be small, or in place of the buffer tank  11  a vent line (not shown) may be provided in a branched manner in the pipe passage  19  (i.e., the vent line may be connected to the pipe passage  19 ). 
     Embodiment 1 
       FIG. 8  is an explanatory diagram for a water vaporization experiment using the vaporizer  1  (whose internal volume is approximately 18 cm 3 ) according to the present invention. The purified water LG in the tank T was pressure-injected into the vaporizing chamber  3  of the vaporizer  1  through an orifice  22  of size/diameter φ=0.8 mm by a pump Pm 2 , and heated by the heating device  6  composed mainly of an I/H heater  13  through the orifice  4   a  of size/diameter φ=0.2 mm and the orifice  4   b  of size/diameter φ=0.2 mm, and the vaporized gas (steam gas) G was passed through the high-temperature type pressure type flow rate control device  2  at a flow rate of 100 SCCM. In addition, the terminal end of a pipe passage  23  on the outlet side of the pressure type flow rate control device  2  was vacuumed by a scroll pump type vacuum pump  21 . 
     The heating device  7  of the high-temperature type pressure type flow rate control device  2  is composed mainly of the cartridge heaters  17  (see, e.g.,  FIG. 4 ), and the heating device  8  of the pipe passage  23 , and the like, is composed mainly of a rubber heater. 
     First, the I/H heater of the heating device  6 , the cartridge heaters of the heating device  7 , and the rubber heater of the heating devices  8  are operated, and it is confirmed that the temperature of the vaporizing chamber  3  is stabilized after preheating of the I/H heater. Thereafter, the supply of the purified water LG was started, and supply of the purified water LG continued until the inner pressure of the vaporizing chamber  3  was maintained at 140 kPa to 160 kPa, and thereafter passed through the pressure type flow rate control device  2 . A setting flow rate of the pressure type flow rate control device  2  is 100 SCCM. Furthermore, flow rate adjustment of the pump Pm 2  was performed so as to maintain the inner pressure of the vaporizing chamber  3  at 140 kPa to 160 kPa. Moreover, the setting pressure at the time of opening the vent valve V 8  was set to 300 kPa. 
     In the above-described experimental state, respectively, the pressures in the vaporizing chamber  3  were measured by the pressure detectors P 01  and P 02 , the pressure in the pipe passage  23  was measured by the pressure detector P 2 , the temperature in the vaporizing chamber  3  was measured by the temperature detector TM 1 , and the outer surface temperature of the control device main body  16  was measured by the temperature detector TM 2 . 
     [Experiment 1] 
     A first vaporization experiment of the purified water LG was performed under the condition that the setting temperature of the heating device  6  (e.g., I/H heater  13 ) of the vaporizer is 160° C., the flow rate of the pump Pm 2  for pressure-feeding liquid is 0.58 cc/min, the setting flow rate of the pressure type flow rate control device  2  is 100 sccm, and the setting temperature of the heating device  7  (i.e., the cartridge heaters  17 ) of the pressure type flow rate control device  2  is 120° C.  FIGS. 9 and 10  show the results of Experiment 1. Respectively,  FIG. 9  shows the relationship between elapsed times, pressures of the respective parts of the system (i.e., chamber inner pressures, and FCS downstream pressure), and flow rates of the pressure type flow rate control device, and  FIG. 10  shows the relationship between elapsed times and temperatures of the respective parts of the system (i.e., chamber internal temperature and chamber surface temperature). 
     [Experiment 2] 
     Another vaporization experiment of the purified water LG was performed under the condition that the setting temperature of the heating device  6  (e.g., I/H heater  13 ) of the vaporizer is 160° C., the flow rate of the pump Pm 2  for pressure-feeding liquid is 0.63 cc/min, the setting flow rate of the pressure type flow rate control device  2  is 100 sccm, and the setting temperature of the heating device  7  (i.e., the cartridge heaters  17 ) of the pressure type flow rate control device  2  is 120° C.  FIG. 11  shows the experimental results for Experiment 2, and shows the elapsed times, the pressures of the respective parts of the system (i.e., chamber inner pressures and downstream pressure), and the flow rates of the pressure type flow rate control device. 
     From the above-described experimental results, it has been understood that: (a) although a pressure fluctuation is slightly brought about in response to the supply of a specific amount of the liquid LG, it is possible to maintain the supply at a stable flow rate by maintaining the pressure in the vaporizing chamber at approximately 150 kPa or more; 
     (b) in the case where the liquid LG is water, the setting temperature of the vaporizing chamber  3  is approximately 160° C., which is sufficient, and when the gas pressure on the outlet side of the vaporizing chamber  3  is 140 kPa or more, it is possible for the pressure type flow rate control device  2  to perform the flow rate control at a constant flow rate regardless of a fluctuation in pressure on the upstream side; 
     (c) it is better to control the pressure in the vaporizing chamber  3  than to control the supply rate of the liquid LG and, therefore, it is preferable that a mechanism for immediately returning released gas to the liquid tank T is provided; and 
     (d) because water cooled in the pipe part so as to be liquefied drops into the vaporizing chamber  3  and causes unstable pressure, it is necessary to take heed of shortening and heating of the pipe on the outlet side of the vaporizing chamber  3 . 
     INDUSTRIAL APPLICABILITY 
     The present invention may be applied to gas supply apparatuses using liquefied gas in all kinds of industries including semiconductor manufacturing, the chemical industry, the medical industry, and the food industry. Furthermore, the present invention may be applied to gas supply apparatuses using all kinds of liquids vaporized by warming as source materials, in addition to water and liquefied gas for semiconductor manufacturing.