HK1090692A - Beverage dispensing apparatus - Google Patents

Description

Beverage dispensing device

The present invention relates to devices for dispensing carbonated or pressurized beverages, and more particularly, to devices for dispensing carbonated or pressurized beverages at higher flow rates with minimal foam generation.

Background

Pressurized beverages, such as beer, are produced by providing the beverage with a quantity of dissolved gas, typically carbon dioxide (CO)₂). Although a certain amount of dissolved CO is naturally produced during beer brewing and fermentation₂Most commercial breweries will dissolve additional CO in their products₂. For a commercial brewery, additional CO is added₂Has two main purposes. First, from a quality control point of view, all beers produced can be adjusted to contain the same amount of CO₂. Second, additional CO₂Providing more sparkling quality to the beer and giving the consumer a better feel and flavor.

Most of the major breweries produce beer containing between 10 and 15psi (68950 and 103425 newtons per square meter) of dissolved CO₂. Because of CO₂Is much lower and tends to release some dissolved CO when the beer is exposed to the surrounding atmosphere₂. Due to the complex chemical constitution of beer, when CO is dissolved₂Foam is generated when leaving the solution.

Other parameters that have an effect on the amount of foam produced in the beer include temperature and turbulence. The physical properties of the liquid indicate that the higher the temperature of the liquid, the smaller the capacity for dissolved gas. Thus, the higher the temperature of the beer, the more readily dissolved gases will escape from the solution, and the more likely the beer will foam. Turbulence and other forms of turbulence can create regions of sudden and abrupt pressure changes in the beer, causing CO₂Spilled from the solution as a foam.

Although many of the beers produced by major commercial breweries tend to be packaged in bottles and cans, large volumes of beer are also packaged in large, sealed containers called kegs. The keg is a reusable and refillable aluminum container that is convenient to use, sanitary, and typically stores and dispenses 15.5 gallons (58.7 liters) of beer. Beer contained in kegs, called keg beer, is commonly served in bars, pubs, night clubs, stadiums, festivals and large parties.

Special devices are required for dispensing the beer keg into an open container at the time of consumption. Beer dispensing faucets (commonly referred to as beer faucets) include valves and spouts for controlling and directing the flow of beer into an open vessel. Beer often foams when it comes out of a conventional faucet. One reason for this foaming is simply because of the CO dissolved in the beer₂And CO in the surrounding atmosphere₂The pressure difference of (a). When beer is exposed to the atmosphere, CO₂Will be naturally released from the beer. Another cause of foaming is the turbulent flow characteristics of beer as it is dispensed through conventional faucets. Even if carefully dispensed, the beer splashes against the walls and bottom of the container to form a foam.

A small amount of foam is often desirable. Beer that is not properly stored will often have dissolved CO₂And then the air is lost to the atmosphere and becomes flat. Thus, a small amount of foam means to the consumer that the beer is fresh. In addition, beer promoters have successfully demonstrated that a perfect beer container should have a rich layer of foam. On the other hand, consumers and beverage vendors do not want excessive foam. Due to CO injected into the vessel₂Foam replaces liquid beer and excess foam can be unsatisfactory to the consumer and often requires another cup. Knowing this, vendors have only two options. They can fill the container with a portion of the beer, wait for the foam to dissipate and then fill it with additional beer, a time consuming process. Alternatively, they may pour out excess foam when filling the container, wasting beer in the process.

Because excessive foam is a problem for both consumers and vendors, attempts have been made to design beer dispensing systems that are installed and configured to achieve an optimal amount of foam during the dispensing process. In addition to maintaining the beer at a constant, cooler temperature throughout the dispensing process, conventional beer dispensing systems are designed to pour the beer at a sufficiently slow flow rate that the beer exiting the faucet hits the container without causing foaming.

The conventional system is optimized for a flow rate of one U.S. gallon (3.785 liters) per minute. While such flow rates are suitable for most small volume dispensing situations, in many cases vendors and consumers would benefit if beer could be dispensed faster while maintaining the optimum amount of foam. In busy bars, pubs, festivals, large parties and sports grounds, consumers have long lines of troops to drink. In these situations, both vendors and customers need to dispense beer faster.

Beer dispensing systems have previously been designed that dispense beer faster than the standard flow rate of one U.S. gallon per minute. One disadvantage of these systems is that they typically use sophisticated electronic controls, making them expensive to manufacture and maintain. Furthermore, some of these systems use storage devices near the faucet, making the device large and difficult to clean. In addition, it is difficult and expensive to install such devices in existing bar counters.

Disclosure of Invention

The present invention relates to a beverage dispensing device that can dispense pressurized beverages at a much higher flow rate than existing mechanical faucet devices without generating excessive foam. It can be implemented entirely in mechanical devices, thereby reducing manufacturing and maintenance costs. In addition, the present invention is installed without the need for storage at or near the dispensing location, thereby facilitating cleaning and retrofitting of existing bar tops.

In a preferred embodiment, the invention comprises a dispensing device for dispensing a pressurized beverage comprising: a spout having an internal passageway through which the pressurized beverage flows at least initially at atmospheric conditions; a liquid receiving end connected as a terminal part of a pressurized beverage dispensing system; and a liquid dispensing end that at least initially dispenses the pressurized beverage to the atmosphere, wherein the cross-sectional area of the internal passageway of the spout decreases from the liquid receiving end to the liquid dispensing end.

In another embodiment, the invention comprises: an upwardly extending neck, a streamlined valve assembly and a downwardly extending nozzle assembly. The overall shape and size of the device allows a series of containers to be filled from the bottom. Furthermore, the nozzle arrangement comprises a streamlined flow-diverting member for dispersing the liquid flow substantially radially. Therefore, the amount of foam generated when beer is dispensed at high speed is reduced.

In one embodiment, the horizontal cross-section of the spout decreases from the top of the spout to the bottom or liquid dispensing end of the spout. Preferably, the reduced cross-sectional profile corresponds to the cross-section of a stream falling under gravity without such a spout. This shape of the spout ensures that liquid flowing therethrough remains substantially in constant contact with the inner wall of the spout. In this way, gas from the liquid dispensing end of the nozzle is prevented from bubbling up into the nozzle. In addition, viscous forces acting between the inner wall of the spout and the liquid flowing through the spout serve to counteract the acceleration of the liquid in the spout caused by gravity.

In another embodiment of the invention, a corrective flow feature is added to the nozzle which can be used to reduce turbulence of the liquid flow through the nozzle. Such components also increase the amount of surface area on which the retarding viscous forces act.

In another embodiment of the invention, the device can select two different flow rates to dispense beer. In such embodiments, a pressure-reducing component and a multi-way valve that can selectively direct liquid through the pressure-reducing component are integrated with the device. When the valve is positioned such that the liquid first flows through the pressure reducer before entering the rapid beverage dispensing device, the dispensing speed of the liquid is reduced, which is preferably the optimal speed for a conventional beer dispensing tap. When the valve is positioned such that liquid bypasses the pressure reducer, the rapid beverage dispensing device operates at a faster flow rate.

Because the rapid beverage device is capable of dispensing beer at a flow rate at least twice that of conventional beer dispensing systems while achieving an optimum level of foam, it also serves as a novel item to attract the attention of beverage consumers. This attraction can be accentuated by making the components of the device of a transparent material so that the beverage flowing therein can be seen by the consumer.

Further advantages and features of embodiments of the present invention may be understood by reference to the following detailed description of the invention in conjunction with the accompanying drawings.

Drawings

Fig. 1 is a side view showing components of a beverage dispensing system with a schematic cross-sectional view of a first embodiment of a rapid beverage dispensing device.

Fig. 2 is a detailed schematic cross-sectional view of the rapid beverage dispensing device of fig. 1.

Fig. 3 is a schematic perspective view of a second embodiment of the rapid beverage dispensing device in which the neck device is replaced by a high drawing dispensing tower.

Fig. 4 is a detailed schematic cross-sectional view of the valve assembly of fig. 2 with the valve in the closed position.

Fig. 5 is a side view of another embodiment of a streamlined valve member for use in the valve assembly of fig. 2.

Fig. 6 is a side view of another embodiment of a streamlined valve member for use in the valve assembly of fig. 2.

Fig. 7 is a schematic cross-sectional view of the valve assembly of fig. 4 with the valve in an open position.

FIG. 8 is a perspective view of the streamlined valve member of FIG. 4 showing the curvature and profile shape of the liquid-facing surface of the valve shoulder.

FIG. 9 is a cross-sectional perspective view of the valve neck and valve shoulder.

FIG. 10 is a schematic cross-sectional view of a conventional beer dispensing faucet.

FIG. 11 is an illustration of the force of gravity acting on liquid flowing out of a conventional faucet.

FIG. 12 shows a schematic cross-sectional view of another embodiment of a nozzle arrangement in which the nozzle, which is linearly tapered, approximates the parabolic profile of the nozzle cross-section of FIG. 2.

FIG. 13 shows a schematic cross-sectional view of another embodiment of a nozzle arrangement in which the cylindrical nozzle approximates the parabolic profile of the nozzle cross-section of FIG. 2.

FIG. 14 is a perspective cross-sectional view of another embodiment of a nozzle assembly wherein the nozzle includes four semicircular corrective flow channels.

FIG. 15 is a cross-sectional view of a nozzle assembly including two semicircular flow-straightening channels.

FIG. 16 is a cross-sectional view of a nozzle assembly including six semicircular flow-straightening channels.

FIG. 17 is a cross-sectional view of a nozzle assembly including seven semicircular flow-straightening channels.

FIG. 18 is a detailed cross-sectional schematic view of the nozzle assembly of FIG. 2 showing the container and the liquid flow lines, indicating that the flow redirector redirects the liquid flow.

Fig. 19 is a perspective view of the flow redirector of fig. 2.

FIG. 20 is a cross-sectional view of another embodiment of a flow redirector for use with the nozzle assembly of FIG. 2.

FIG. 21 is a cross-sectional view of yet another embodiment of a flow redirector for use with the nozzle assembly of FIG. 2.

FIG. 22 is a cross-sectional view of yet another embodiment of a flow redirector for use with the nozzle assembly of FIG. 2.

FIG. 23 is a schematic cross-sectional view of a nozzle assembly having a flow redirector with longitudinally adjustable position.

FIG. 24 is a schematic cross-sectional view of the nozzle assembly of FIG. 23, with the flow redirector shown moved to a new position.

Fig. 25 is a schematic cross-sectional view of a rapid beverage dispensing device having a conical diffuser in its neck assembly.

Fig. 26 is a schematic cross-sectional view showing a rapid beverage dispensing apparatus with a multi-way valve and a pressure reducing member.

Fig. 27 is a detailed schematic cross-sectional view of the multi-way valve of fig. 26, wherein the valve directs liquid around the pressure reduction member.

Fig. 28 is a detailed schematic cross-sectional view of the multi-way valve of fig. 26 directing liquid through a pressure relief feature prior to directing the liquid to the rapid beverage dispensing apparatus.

Detailed Description

As shown in fig. 1, the rapid beverage dispensing device 35 includes a neck assembly 36, a valve assembly 37 and a downwardly extending nozzle assembly 38. In a preferred embodiment, the neck assembly 36 is substantially vertical. The rapid beverage dispensing device 35 is designed to be connected to a conventional pressurized beverage dispensing system, such as a beer dispensing system 39, which includes: a beer keg 40 or similar beverage storage means and a beverage tube 41 for transporting beverage from the container or keg 40 to the rapid beverage dispensing device 35. A handle (shank)42 connects the rapid beverage dispensing device 35 to the beverage tube 41. A keg lead-out 43 connects the beverage tube 41 to the beer keg 40. The dip tower 44 supports the handle 42.

Most major producers in the united states produce beer that is formulated to be optimally stored and served at approximately 38 degrees fahrenheit (3.3 degrees celsius). If the beer is warmer than this optimum temperature, it will release too much carbon dioxide (CO) upon dispensing₂). If the beer is cooler than the optimum temperature, it will retain too much CO when dispensed₂And thus, the taste is weak. Because most systems are not capable of maintaining precise temperatures, a range between 36 and 40 degrees Fahrenheit (2.2 and 4.4 degrees Celsius) is generally acceptable. Accordingly, in one embodiment, the beer dispensing system 39 of the present invention is capable of cooling and maintaining the various components of the system within an acceptable temperature range.

As shown in fig. 1, in many dispensing systems, the beer in the beverage tube 41 can be kept cool by circulating a cooling fluid through a cooling fluid tube 45 bundled with the beverage tube 41. Such systems typically utilize a glycol cooling device 46 and a glycol pump 47 to cool and circulate the glycol. Alternatively, some systems blow cool air through a conduit that includes the beverage tubing 41 as a means of keeping the beverage tubing 41 cool.

The beer in the beer keg 40 requires an energy source in order to transfer the beverage from the beer keg 40 through the entire beer dispensing system 39 to the rapid beverage dispensing system 35. The energy source is usually provided by compressing a gas (usually compressed CO)₂) To provide. As shown in FIG. 1, in the system, compressed CO is filled₂The canister 48 is connected to the beer keg 40 by a compressed gas hose 49. Pressure regulating device 50 serves to regulate CO driving beer through beer dispensing system 39₂And (3) a pressure device. In systems where the distance between the beer keg 40 and the rapid beverage dispensing device 35 is large, a second gas can be used to provide additional pressure for delivering beer through the beverage tube 41. Compressed nitrogen (N) gas contained in the nitrogen gas tank 51₂) May be used as the second gas. The nitrogen tank 51 is connected to the beer keg 40 by a separate compressed gas hose 49. A separate pressure regulating device 50 serves as a means for regulating the additional pressure provided by the compressed nitrogen. Some systems may extract nitrogen from air, thus eliminating the need for a separate nitrogen tank. Alternatively, in another embodiment, the system may use a mechanical pump (not shown) to provide the energy required to transport beer through the system, instead of, or in addition to, the compressed gas.

Reynolds number is a dimensionless parameter commonly used in liquid flow analysis. Liquids flowing through circular pipes or tubes with reynolds numbers below 2100 will exhibit laminar flow. Systems with reynolds numbers greater than 4000 may exhibit turbulent flow. Systems that are neither laminar nor turbulent will exhibit excessive flow characteristics. The Reynolds number can be calculated by the following equation:

where Re is Reynolds number

Rho ═ liquid density

Linear velocity of liquid

D is the diameter of the pipe

Viscosity of liquid

The pressure drop experienced by the liquid flowing through the rapid beverage dispensing device 35 is one of several parameters that determine the flow rate of beer through the beer dispensing system 39. The flow rate is also determined by the length, diameter and roughness of the beverage tube 41, the height difference between the beer keg 40 and the rapid beverage dispensing device 35, and the compressed CO₂And/or N₂The influence of the supplied energy. Specifically, for a fully developed laminar flow of liquid, the flow rate may be determined according to the following equation:

wherein Q is the volumetric flow rate

D is the diameter of the beverage tube 41

Δ p ═ pressure difference between beer keg 40 and rapid beverage dispensing device 35

Mu-viscosity of the beer or other liquid dispensed

I-length of beverage tube 41 through which beer flows

The target flow rate for a conventional beer dispensing faucet is one U.S. gallon (3.785 liters) per minute, while the target flow rate for the rapid beverage dispensing device 35 is at least twice that rate. Whether the beer is flowing at one gallon per minute or three gallons per minute, for beverage tubing 41 having an inner diameter of less than 1 inch, the flow through the beverage tubing 41 is difficult to achieve a completely laminar flow. In these cases, the following formula applies:

wherein

h_LHead loss between system parts 1 and 2

f-coefficient of friction (function of roughness and Reynolds number of the beverage pipe 41)

Length of the beverage tube 41

D-diameter of the beverage tube 41

Linear velocity of liquid

g is universal gravitation constant

Therefore, as the length of the beverage tube 41 connecting the beer keg 41 and the rapid beverage dispensing device 35 increases and the diameter of the beverage tube 41 decreases, the compressed CO must be increased₂And/or N₂The amount of energy provided is such that the head loss of the additional pressure is overcome. In addition, the compressed CO must be added₂And/or N₂The amount of energy provided increases the speed of the liquid flow through the beverage tube 41. Preferably, the beer dispensing system 39 is designed to deliver beer at an increased flow rate to the handle 42 so that the quick dispense system 35 provides increased priming capability as compared to conventional systems.

The neck assembly 36 of the rapid beverage dispensing device 35 positions and supports the rapid beverage dispensing device 35 so that multiple sized containers from glass to can be filled at the bottom (bottomfilling). For bottom filling such containers, the distance between the end 52 of the nozzle assembly 38 and the top of the bar 53 or other structure directly below it is preferably at least as great as the height of the largest container to be placed. Preferably, sufficient clearance is required to place canister 54 directly under nozzle assembly 38.

Fig. 2 shows in more detail one embodiment of the rapid beverage dispensing device 35 of the present invention. In the embodiment shown in FIG. 2, the lower end 55 of the neck assembly 36 is threaded 56 and is connected to a standard beer faucet shank 42 by a standard shank coupling nut 57, compression ring 58 and compression washer 59, although other connection methods may be used, including but not limited to the use of a flange with an O-ring and a quick disconnect. Additionally, the neck assembly 36 may be permanently attached to the handle 42 by welding or other methods. The handle 42 is connected to the dip dispensing tower 60, typically when the bar top is installed. A coupling gasket 61 is interposed between the shank 42 and the neck assembly 36 to ensure a tight seal. In the neck assembly is the length of neck tube 62 that carries liquid from handle bore 63 to valve assembly 37. The diameter of the neck tube 62 preferably matches the diameter of the shank bore 63 at the point of connection between the neck assembly 36 and the shank 42. Preferably, the neck tube 62 at the lower end 55 of the neck assembly 36 is initially axially aligned with the shank bore 63. In this embodiment, the neck tube 62 is bent approximately 90 degrees before remaining perpendicular in the neck assembly 36. The neck tube 62 is then bent into an arc 64 of approximately 90 degrees near the upper end 65 of the neck assembly 36. As the radius of arc 64 increases, the turbulence associated with the change in direction of the fluid flow decreases. Although the circular arc 64 having a larger radius reduces turbulence associated with changes in direction of liquid flow, it also results in a larger horizontal distance between the dip tower 44 and the nozzle assembly 38 for the rapid beverage dispensing apparatus 35. Thus, the radius of the arc 64 is preferably small enough so that the nozzle assembly 38 can be placed directly on the bar top discharge assembly 66. In a preferred embodiment, valve assembly 37 is connected to an upper end 65 of neck assembly 36 such that liquid can flow through neck tube 62 into valve assembly 37 without leaking. Additionally, the neck tube 62 at the upper end 65 of neck assembly 36 may have an increased inner diameter as it approaches valve assembly 37 such that the inner diameter of neck tube 62 mates with the inner diameter of valve housing 94 at the location where neck assembly 36 and valve assembly are joined.

Since neck assembly 36 is exposed to the ambient environment, the beer remaining in neck tube 62 during system shut-down may become undesirably warm. In order to maintain the draught beer in the neck tubing 62 at the proper serving temperature, the neck assembly 36 may be filled with insulation 67. Alternatively, or in addition to the insulation 67, the neck assembly 36 may be cooled with glycol by extending a coolant line 45 into the neck assembly 36 (not shown).

In another embodiment of the present invention, as shown in fig. 3, the neck assembly 36 of the rapid beverage dispensing device 35 is replaced by a tall dip dispensing tower assembly 68 comprising a tall dip dispensing tower 69, a dip dispensing tower lid 70, a dip dispensing tower base 71, mounting screws 72, shank 42 and cylindrical insulation 73. In this embodiment, the valve arrangement 37 is connected to a handle 42 that is secured to a high draft dispensing tower 69. The valve assembly 37 may be attached to the shank 42 using a shank coupling nut 57, a compression ring 58, a compression washer 59, and a coupling washer 61, although other means, including a flange with an O-ring and quick disconnect, may be used. The distance between the bar top 53 and the handle 42 is such that the distance between the end 52 of the nozzle assembly 38 and the bar top 53 is greater than the height of the standard can 54. In this embodiment, there is no neck assembly exposed to the ambient environment, and the beer remaining at the pressure upstream of the valve assembly 37 remains insulated from the ambient environment in the high draft dispensing tower assembly 68. Additionally, in this embodiment, the diameter of the handle bore 63 gradually increases along its length such that at one end the diameter of the handle bore 63 is the same as the diameter of the beverage tube 41, and the diameter of the handle bore 63 and the inner diameter of the valve housing 94 cooperate at the point where the valve assembly 37 joins the handle 42.

As shown in FIG. 4, in one embodiment, valve assembly 37 includes a valve member 74, a handle lever 75, a friction ring 76, a bonnet washer 77, a compression bonnet 78, a valve cavity 79, a valve seat 80, a valve shoulder guide 81, an outer vent 82, and an inner vent 83. Valve member 74 may include a valve head 84, a valve neck 85, a valve shoulder 86, and a seat gasket 87. Valve neck 85 may be secured to valve head 84 by any known means. Preferably, the valve neck 85 is threadably secured to the valve head 84 so that the two parts can be disassembled. A seat gasket 87 may be positioned between valve head 84 and valve neck 85. The contour shapes of the assembled valve head 84, seat gasket 87 and valve neck 85 are streamlined to minimally interfere with the liquid flowing therearound. Thus, the outer liquid-facing surface 88 of seat washer 87 transitions smoothly, preferably tangentially, to the outer surface 89 of valve head 84. In addition, the outer surface of the seat gasket 87 facing the liquid transitions smoothly, preferably tangentially to the valve neck 85.

Fig. 5 and 6 show other embodiments of the valve member 74. In these embodiments, the valve head 84 is characterized by a substantially spherical or elliptical shape, with the outer surface 88 of the seat gasket 87 generally contoured to smoothly transition into the outer surface 89 of the valve head 84. In addition, the contour of the outer surface of the seat gasket 87 generally smoothly transitions into the valve neck 85. As shown in FIG. 4, the valve shoulder 86 may be sized to slide longitudinally into the shoulder guide 81 with a tight circumferential tolerance so that the entire valve member 74 is axially aligned with the valve chamber 79. The end 90 of the handle lever 75 fits into the valve shoulder slot 91. A ball joint 92 embedded in the handle lever 75 is seated in a ball seat 93 forming part of a valve housing 94. Friction ring 76 and bonnet washer 77 fit circumferentially around the upper end of ball joint 92. The compression bonnet 78 may also fit circumferentially around the handle stem 75 and be secured by threads of the compression bonnet 78 and threads in the valve housing 94. When threaded into position, compression bonnet 78 bears against friction ring 76 and bonnet washer 77, forming a seal that prevents beer from leaking out of valve assembly 37 through ball seat 93.

Fig. 4 shows the valve arrangement 37 with the valve member 74 in the closed position. In this position, the proximal threaded end 95 of the handle lever 75 may be angled toward the valve head 84. Because the handle lever 75 pivots about its ball joint 92, in the valve closed position, the distal end 90 of the handle lever 75 is angled away from the valve head 84, thereby pulling the valve member 74 longitudinally until the seat washer 87 contacts the valve seat, thereby forming a seal that shuts off the flow of liquid. In this position, the pressure of the liquid in the valve chamber 79 and through the system will be greater than the ambient atmospheric pressure to prevent CO from being released when the system is not pouring beer₂Overflow from the solution. Thus, the liquid in the valve chamber 79The combination of pressure and friction between valve shoulder 86 and valve shoulder guide 81, as well as the friction between valve shoulder groove 91, friction ring 76, bonnet washer 77, compression bonnet 78 and handle lever 75 is sufficient to hold valve member 74 in its closed position. Therefore, no spring, lock, actuator, or other member is required to exert a positive force on the valve member to hold the valve member 74 in its closed position, regardless of the pressure of the liquid upstream of the valve member 74. In addition, when the valve member 74 is in the closed position, the valve shoulder groove 91 forms a channel between the outer vent aperture 82 and the inner vent aperture 83 to allow air to enter the upper portion of the spout, which promotes a more rapid and complete removal of any liquid from the spout assembly 38 when the valve member 74 is moved to the closed position.

To open the valve member 74, the threaded end 95 of the handle lever 75 is moved forward in a direction generally away from the valve seat 80. Because the handle lever 75 moves in this manner, it pivots in the ball seat 93 about the center of the ball joint 92, causing the end 90 of the handle lever 75 to rotate in the opposite direction. Movement of the tip 90 of the handle lever 75 slides the valve member 74 in a direction to move the seat washer 87 away from the valve seat 80, thereby placing the valve member 74 in the open position. The force exerted on valve head 84 by the fluid flowing therearound, in combination with the frictional forces between valve shoulder 86 and valve shoulder guide 81, and between valve shoulder groove 91, friction ring 76, bonnet washer 77, compression bonnet 78 and handle lever 75, is sufficient to hold valve member 74 in its open position without the need for continuous active force to be applied to handle lever 75 or valve member 74.

Preferably, the valve means 37 are designed as streamlined as possible in order to reduce disturbances in the liquid flow. As indicated by the fluid flow lines 96 in fig. 7, the fluid directed through the valve assembly 37 arcs into the generally downwardly directed nozzle assembly 38. Thus, the valve member 37 should not only be able to open and stop the flow of liquid, but should also minimize disturbance of the flow of liquid as it is directed into the spout 99. To promote smooth redirection of fluid flow, as shown in fig. 8, the fluid-facing surface 97 of valve shoulder 86 is contoured to match the curvature of the inner surface of valve housing 94 when valve member 74 is in the open position. Specifically, in the embodiment shown herein, the inner surface of valve housing 94 proximate valve shoulder 86 is generally shaped as a portion of an arcuate cylinder. That is, the liquid facing surface 97 of the valve shoulder 86 is generally concave in shape and has two radii of curvature. The first radius matches the larger radius of the arc formed by the valve housing 94 directing liquid into the orifice 99. The second radius of curvature is perpendicular to the first radius and mates with the inner diameter of the valve housing 94 where the valve member 37 and nozzle 99 join. Alternatively, the liquid-facing surface 97 of the valve shoulder 86 may have only the first radius of curvature, in which case the liquid-facing surface 97 of the valve shoulder 86 may still direct liquid into the spout 99 in a streamlined fashion. Alternatively, the liquid-facing surface 97 of valve shoulder 86 may be planar, in which case the edge of this plane should be flush with the inner surface of valve housing 94 when valve member 74 is in the open position, and the plane is inclined to an extent effective to direct liquid into orifice 99. In contrast, as shown in FIG. 10, in a conventional beer dispensing faucet 98, the liquid-facing surface 97 of the valve shoulder 86 is a flat, generally vertical plane. In addition, such a design can result in the liquid changing direction abruptly, as indicated by the liquid flow lines 96. This sudden redirection of the liquid causes turbulence.

Because some of the liquid flowing through the valve chamber 79 must pass through the valve neck 85 on its way into the nozzle assembly 38, the cross-section of the valve neck 85 is streamlined to facilitate the flow of liquid in this direction, as shown in FIG. 9.

In addition to the above-described embodiment of manually moving the valve member 74, the energy required to move the valve member between the open and closed positions will also be provided in an automatic or engine-operated manner. For example, in one embodiment, the push-pull function of the handle lever 75 in moving the valve member 74 from its closed position to its open position and back may be replaced with a linear actuator connected to the valve shoulder 86. In addition, the valve member 74 may also be moved electromagnetically in a manner similar to a solenoid controlling water flow in a household appliance. Also, a gear or other rotary valve moving mechanism may also function to move the valve member 74 between the closed and open positions.

Preferably, the liquid flowing through the valve means 37 is immediately directed into the nozzle means 38, as shown in fig. 2. Preferably, the nozzle assembly 38 includes a downwardly extending nozzle 99 and a liquid dispersion member or flow diverter 100 positioned near a lower end 101 of the nozzle 99. The liquid flowing through the valve means 37 into the nozzle means 38 is accelerated by the effect of gravity. The nozzle assembly 38 serves four primary functions. First, the viscous forces between the nozzle inner surface 102 and the liquid can slow the liquid flow, somewhat counteracting the acceleration of the liquid due to gravity. Second, the shape of the nozzle inner surface 102 is designed to reduce the chance of air entering the system upwardly when the valve member 74 is in its open position. The solid, air-free flow reduces liquid foam in the nozzle assembly 38. Third, the flow redirector 100 is configured to redirect the flow of liquid exiting the nozzle assembly 38, reducing turbulence and foaming that may otherwise occur as the liquid impacts the interior surface of the filled container. Preferably, the nozzle assembly 38 is long enough so that the diverter 100 can contact the bottom of the largest container being filled, thereby enabling filling from and near the bottom of the container. In a preferred embodiment, the nozzle assembly 38 is about 3 inches (7.62 cm) to about 15 inches (38.1 cm) in length. More preferably, the nozzle assembly 38 has a length of about 4 inches (10.16 cm) to about 12 inches (30.48 cm). More preferably, the nozzle assembly 38 is about 8 inches (20.32 cm) to 10 inches (25.4 cm) in length.

Fig. 11 shows the flow 103 from the conventional faucet 98. Absent the spout 99, the liquid in the faucet 98 increases in flow rate as the liquid falls due to gravity. This acceleration causes the cross-sectional area of the stream 103 to decrease as the liquid falls and moves further and further away from the faucet 98. The general shape of its profile is parabolic, and its specific profile depends on the flow rate of the liquid and the diameter of the faucet outlet 104. Using the basic principles of geometry, the cross-sectional area of the stream 103 can be calculated for a given distance from the faucet outlet 104 using Bernoulli's equation. According to the Bernoulli formula (Bernoulli's equation):

wherein p is₁、p₂Hydraulic pressure at the tap outlet 104 and at a distance from the tap outlet 104, respectively

ρ is the density of the liquid

V₁、V₂Linear velocities of liquid stream 103 at faucet outlet 104 and at a distance from faucet outlet 104, respectively

g is acceleration due to gravity

z₁And z₂Respectively, at the tap outlet 104 and at a given distance from the tap outlet 104

Since the free-flowing liquid stream 103 is at atmospheric pressure, p₁＝p₂0. Setting z₁＝0，z₂H, mixing V with₂Renamed as V₀，V₁Renamed as V_hProviding V_hEquation for h, where V_hIs the linear velocity of the stream 103 at a vertical distance h below the faucet outlet 104.

Wherein V₀Is the linear velocity of the stream 103 at the faucet outlet 104.

The relationship between the flow velocity of the liquid stream 103 and the linear velocity of the liquid stream 103 and the cross-sectional area of the liquid stream 103 is as follows according to the following equation:

Q＝A₀V₀

wherein Q is the flow rate of the liquid

A₀Is the cross-sectional area of the faucet outlet 104

V₀Is the linear velocity of the liquid stream 103 at the faucet outlet 104

Find V₀And in relation to V_hSubstituting in the equation of (a), yields the following result:

for a circular faucet spout 104, A₀Can be composed of₀Expression of D₀Is the diameter of the faucet outlet 104:

further substitution is made to find D₀V of_h：

Furthermore, because the flow rate of the liquid is constant in an uncompressed system:

Q＝A_hV_h

wherein Q is the volumetric flow rate of the liquid

A_hIs the cross-sectional area of the stream 103 at a distance h from the faucet outlet 104

V_hIs the linear velocity of the stream 103 at a distance h from the faucet outlet 104

Determine A as described above_hAnd using the previously determined V_hInstead, the cross-sectional area V of the liquid stream 103_hI.e. as a function of its vertical distance h from the tap outlet 104, the diameter of the tap outlet 104 and the liquid flow rate:

Q＝V_hA_h

preferably, the cross-sectional shape of the nozzle assembly 38 matches the cross-sectional shape of the free-falling liquid stream 103, as calculated using the above equation. In this embodiment, the cross-sectional area of the spout 99 gradually decreases from top to bottom. In the preferred embodiment using a flow redirector, the nozzle 99 widens near its distal end to accommodate the flow redirector 100, but the resulting concentric ring cross-sectional area maintains a continuum of decreasing cross-sectional areas to the nozzle assembly outlet 105. As shown, the concentric rings can maintain a gradual decrease in cross-sectional area through the use of flow redirectors in which the cross-sectional area of the flow redirector shaft 106 gradually increases from top to bottom. Alternatively, the diameter of the flow redirector shaft 106 of the flow redirector 100 may be fixed if the cross-section (not shown) of the end of the nozzle 99 is tapered. The nozzle assembly 38 having a cross-sectional shape that matches the cross-sectional shape of the free-falling liquid stream 103 allows liquid flowing through the nozzle assembly 38 to remain in constant contact with the nozzle interior surface 102. In this way, friction forces acting between the liquid and the nozzle inner surface 102 may slow the liquid down. In addition, air cannot enter the nozzle assembly 38 in the form of bubbles as long as the liquid is flowing at the optimized flow rate of the nozzle assembly 38.

In an alternative embodiment of the nozzle assembly 38 shown in fig. 12, the nozzle 107 has a linear taper approaching the decreasing cross-sectional area of the nozzle 99, the cross-sectional shape of the nozzle 99 matching the cross-sectional shape of the free-flowing stream.

In another embodiment of the nozzle assembly 38 shown in FIG. 13, a cylindrical nozzle 108 is used. In this embodiment, the cross-sectional area of the cylindrical orifice 108 is constant until the flow redirector 100 is introduced, in which case the reduction in cross-sectional area caused by the flow redirector 100 is sufficient to prevent air from entering the cylindrical orifice 108 as the liquid flows. Thus, the cross-sectional area of the internal passageway decreases from the liquid receiving end of the spout to the liquid dispensing end of the spout.

In another embodiment as shown in FIG. 14, the nozzle assembly 38 includes two or more flow-straightening channels 109 for reducing the radial movement of liquid in any nozzle assembly 38 and for reducing turbulence of the liquid flowing through the nozzle assembly 38. The nozzle 99 is preferably divided into at least two channels 109, and preferably three to ten channels 109. It is more preferable to divide the nozzle 99 into four channels 109 of equal size. Figures 15, 16 and 17 show cross-sections of various embodiments of nozzles having channels.

The reynolds number indicates a laminar or turbulent state of the liquid flow. The Reynolds number for a circular cross-section nozzle 99 without a flow-straightening channel 109 can be expressed as follows:

the reynolds number for a non-circular conduit may be determined by the equation:

wherein Re_hIs the reynolds number based on hydraulic diameter. Hydraulic diameter of D_hWhere a is the cross-sectional area of the catheter and P is the circumference of the catheter. For each equally sized semi-circular wedge-shaped channel 109 in the nozzle assembly 38:

where D is the inside diameter of the nozzle 99 and n is the number of semi-circular wedge channels 109 of the same size. The Reynolds number for the orifice 99 with the channels 109 compared to the orifice 99 without any flow-straightening channels yields the following ratio:

thus, the Reynolds number of the liquid flowing through the nozzle assembly 38 with the flow-straightening channels 109 is reduced by the factor (π)/(π + n) compared to the nozzle assembly 38 without flow-straightening channels. As noted, increasing the number of channels 109 may further reduce the reynolds number of the liquid flowing through the nozzle 99. In addition, the surface 110 of each flow-straightening channel 109 increases the effective surface area on which viscous forces developed between the liquid and the surface 110 can act, thereby further decelerating the liquid as it flows through the orifice 99.

The nozzle assembly 38 may be insulated and/or cooled by liquid or other means known in the art, including, but not limited to, sponge, air, circulating glycol, circulating water, and thermoelectric devices. Because the nozzle assembly 38 is exposed to ambient air, it would be heated to ambient temperature without such insulation or cooling mechanisms. The glycol line of the glycol-cooled dispensing system may also be extended to wrap around the nozzle assembly 38 (not shown) to cool the nozzle assembly 38.

The primary reason for excessive foaming during beer dispensing is to cause the beverage to impinge on the bottom of the container at a relatively rapid rate or in another turbulent manner. The flow redirector 100 thus reduces the generation of foam by gradually redirecting and dispersing the liquid exiting the nozzle assembly 38, thereby reducing the impact force between the liquid and the container. As shown by the simulated liquid flow lines 96 in fig. 18, the liquid flowing through the nozzle assembly 38 is evenly distributed around the flow redirector shaft 106. As the liquid flows through the flow redirector 100, it gradually redirects to radial flow from a generally downward direction. Preferably, the liquid flowing from the nozzle assembly 38 is dispersed radially in an average 360 degree pattern including a downward vector. It has been determined that this approach minimizes foaming of the beverage when dispensing liquids for various sized containers. A lip 111 may also be provided at the lower end of the spout 99. Lip 111 is preferably rounded to improve the flow characteristics of the liquid exiting the nozzle assembly outlet 105, although other shapes may be used.

Preferably, the flow redirector 100 is a streamlined object. In a preferred embodiment, the proximal end 112 of the flow redirector 100 is in the shape of an elliptical dome. In this embodiment, the circular flow redirector shaft 106 is gradually widened toward the flow redirector base 113 to minimize turbulence as the flow is redirected. Preferably, the flow redirector 100 is circular in horizontal cross-section throughout its longitudinal length, but other shapes are contemplated as long as they do not significantly interfere with the flow of liquid. The flow redirector base 113 is also preferably circular and flat so that the bottom of a flat-bottomed container can be placed flush against the flow redirector base 113. However, the bottom of the diverter seat 113 may also be a slightly concave surface, as long as the outer edge of the bottom of the flow diverter seat 113 is in sufficient contact with the bottom of the container to be filled. The outer surface of the flow redirector 100 is preferably smooth.

While a taller and wider flow redirector 100 may reduce turbulence as the liquid is redirected, such a flow redirector 100 may result in a nozzle assembly 38 that is longer and wider and therefore difficult to use with smaller containers. For this reason, a more compact flow redirector 100 is needed. Preferably, the flow redirector 100 is between 0.5 inches (1.27 centimeters) and 8 inches (20.32 centimeters) when measured between its proximal end 112 and the seat 113. More preferably, the flow redirector 100 is between 1 inch (2.54 centimeters) and 4 inches (10.16 centimeters) when measured along the length. More preferably, the flow redirector 100 is 2 inches (5.08 centimeters) when measured along the length. Preferably, the flow redirector base 113 measures between 0.25 inches (0.635 cm) and 5 inches (12.7 cm) at its widest point. More preferably, the flow redirector base 113 measures between 0.5 inches (1.27 centimeters) and 2 inches (5.08 centimeters) at its widest point. Fig. 20, 21 and 22 show other embodiments of the flow redirector 100. There are many other shapes and configurations of the flow redirector 100 that reduce the amount of foam generated when liquid exits the nozzle assembly 38 and impacts a container. The flow redirector is preferably of an inverted cone shape.

Preferably, the flow redirector 100 is generally not movable, but can be disassembled. The flow redirector 100 may be connected to the inside of the nozzle 99 by one or more support structures 114. The support structure 114 is of sufficient strength to center the flow redirector 100 along the axis of the spout 99, even when a liquid flow is present. To reduce interference with fluid flow, the support structure 114 is preferably streamlined and includes a rounded proximal end 115 that tapers to a point at the distal end 116. It has been found that the airfoil shape shown in FIG. 19 minimizes turbulence caused by the support structure 114. Where the nozzle assembly 38 includes a flow-straightening channel 109, the flow redirector 100 may not need a support structure 114 to be fixedly positioned, as it may be directly fixed to the surface 110 forming the flow-straightening channel 109.

The flow redirector 100 is positioned longitudinally within the nozzle assembly 38 such that a nozzle assembly outlet 105 is formed between the lip 111 of the nozzle assembly 38 and the flow redirector 100 to allow liquid to exit the nozzle assembly 38 into a container. The size of the nozzle assembly outlet 105 must be large enough to allow the liquid to flow rapidly out of the nozzle assembly 38, and yet small enough to allow even radial dispersion of the liquid into the container. The optimum size of the nozzle assembly outlet 105 will vary with the liquid flow rate, the diameter of the nozzle 99 and the particular shape of the flow redirector 100. Preferably, the height of the nozzle assembly outlet 105 is between 0.2 inches (0.508 cm) and 1.5 inches (3.81 cm) when measuring the vertical distance between the lip 111 of the nozzle 99 and the flow redirector 100. More preferably, the height of the nozzle assembly outlet 105 is between 0.35 inches (0.889 cm) and 0.6 inches (1.524 cm). More preferably, the height of the nozzle assembly outlet 105 is between 0.4 inches (1.016 cm) and 0.5 inches (1.27 cm).

While the height of the nozzle assembly outlet 105 may be a fixed distance, another embodiment of the present invention as shown in fig. 23 and 24 allows for fine adjustment of the particular longitudinal position of the flow redirector 100 in the nozzle assembly 38 using a set screw 117 and a countersunk slot 118 in the nozzle 99, with the flow redirector 100 being movable in the longitudinal direction by loosening the set screw 117. Moving the flow redirector 100 longitudinally along the axis of the nozzle assembly 38, the height of the nozzle assembly outlet 105 will change. The set screw 117 may also be completely removed from the nozzle assembly 38 so that the flow redirector 100 may be completely removed from the nozzle assembly 38 for cleaning and maintenance.

In another embodiment of the invention, a diffuser 121 is placed upstream of the valve assembly 37 to increase the cross-sectional area of the liquid entering the valve assembly to minimize turbulence. Preferably, the diffuser 121 tapers from its throat end 119 to its outlet end 120. In one embodiment, as shown in FIG. 25, a conical diffuser 121 is placed in the neck assembly 36 of the rapid beverage dispensing device 35. In this embodiment the axis of the conical diffuser 121 is vertically aligned with the neck assembly 35 of the rapid beverage dispensing device 35, although it may also include a radius of curvature. Preferably, the divergence angle of the conical diffuser 121 (the angle measured between the axis of the conical diffuser 121 and the conical diffuser wall 122) is small. A larger divergence angle often results in increased turbulence because the cross-sectional area of the liquid is forced to increase over a shorter distance. To reduce turbulence while facilitating dispensing, the divergent angle of the conical diffuser 121 is preferably less than 25 degrees. More preferably, the divergence angle is less than 12 degrees, and more preferably is an angle of 8 degrees or less.

In certain situations, it is desirable to slow the flow rate of liquid exiting the rapid beverage dispensing device 35. In another embodiment of the present invention, as shown in FIG. 36, a pressure reducing member 123 and a multi-way valve 124 are incorporated into the system in order to selectively slow the flow rate of the liquid dispensed. Although the pressure reducing member 123 may take various forms, preferably, the pressure reducing member 123 is comprised of a length of tubing having a relatively narrow diameter. The pressure-reducing member 123 is coiled within the neck assembly 36 of the rapid beverage dispensing device 35, thereby reducing the space required therefor.

The input 125 and output 126 of the pressure-reducing element 123 are connected to a multi-way valve 124 disposed in a neck seat 127 of the rapid beverage dispensing device 35. In one position, the multi-way valve 124 provides a full-port opening (full-port opening) between the rapid beverage dispensing device 35 and the rest of the beer dispensing system 39, as shown in the embodiment of fig. 27. Flow arrows 128 indicate the path of the fluid through the multi-way valve 124. In this position, the flow of liquid bypasses the pressure reducing member 123 entirely and liquid is dispensed from the rapid beverage dispensing device 35 at a conventional flow rate as if the pressure reducing member 123 were not present.

In other positions, as shown in fig. 28, the multi-way valve 124 directs the liquid through the pressure-reducing member 123 as it passes through the quick drink assembly 35. In this position, liquid entering the multi-way valve 124 is directed to the valve's output port 129, which is connected to the input port 125 of the pressure reducing member 123. Energy from the beer dispensing system 39 continues to move the liquid through the entire length of the pressure reducing element 123 before the liquid reenters the multi-way valve 124 through its valve input port 130 which directs the liquid from the output 126 of the pressure reducing element 123 through the rapid beverage dispensing device 35. Because the pressure of the liquid reentering the multi-way valve 124 drops, the liquid reenters the rapid beverage dispensing device 35 at a reduced flow rate (preferably the optimal flow rate for conventional beer dispensing faucets).

The foregoing detailed description is to be considered as illustrative and not restrictive, and it is understood that the spirit and scope of the invention is defined by the following claims (including all equivalents).

Claims (57)

1. A beverage dispensing device for dispensing a pressurized beverage, comprising: a nozzle through which the pressurized beverage exits to the atmosphere at least initially, the nozzle having an internal passage; a liquid receiving end connected as a terminal part of a pressurized beverage dispensing system; and a liquid dispensing end for dispensing the pressurized beverage to the atmosphere at least initially, wherein the cross-sectional area of the internal passageway of the spout decreases from the liquid receiving end to the liquid dispensing end.

2. The beverage dispensing apparatus of claim 1 wherein the decrease in cross-sectional area of the internal passage is continuous.

3. The beverage dispensing apparatus of claim 2 wherein the cross-sectional profile of the internal passage approximates the cross-sectional profile of a free falling stream of liquid at ambient pressure.

4. The beverage dispensing device of claim 2 wherein the length of the nozzle is at least about 3 inches.

5. The beverage dispensing apparatus of claim 4 wherein liquid flowing through the nozzle is in substantially continuous contact with a surface of the internal passage.

6. The beverage dispensing device of claim 1 including a liquid dispersion member having a liquid receiving end and a liquid dispersion end, said liquid dispersion end extending from said liquid dispensing end of said nozzle and radially dispersing beverage flowing from said liquid dispensing end of said nozzle.

7. The beverage dispensing device of claim 6 wherein the liquid dispersion member is removably supported within the liquid dispensing end of the internal passage of the nozzle.

8. The beverage dispensing apparatus of claim 6 wherein the liquid dispersion member further comprises a stem having a substantially uniform periphery and a liquid dispersion surface having a generally inverted cone shape.

9. The beverage dispensing device of claim 8 wherein the liquid dispersing surface of the liquid dispersion member extends from the liquid dispensing end of the nozzle from about 0.2 inches to about 1.5 inches.

10. The beverage dispensing device of claim 9 wherein the liquid dispersing surface of the liquid dispersion member extends from the liquid dispensing end of the nozzle from about 0.35 inches to about 0.6 inches.

11. The beverage dispensing device of claim 10 wherein the liquid dispersing surface of the liquid dispersion member extends from the liquid dispensing end of the nozzle from about 0.4 inches to about 0.5 inches.

12. The beverage dispensing apparatus of claim 6 wherein the distance that the liquid dispersion surface of the liquid dispersion member extends from the liquid dispensing end of the nozzle is adjustable.

13. The liquid dispersion member of claim 8 wherein the liquid dispersion surface has a gradually decreasing slope.

14. The liquid dispersion member of claim 13 wherein the liquid dispersion surface disperses liquid from the nozzle at an angle relative to a longitudinal axis of the nozzle.

15. The liquid dispersion member of claim 14 wherein the dispersing surface disperses liquid from the nozzle substantially perpendicular to an axis of the liquid dispersion member.

16. The beverage dispensing apparatus of claim 1 wherein the cross-sectional profile of the internal passage decreases progressively from top to bottom according to the following equation:

17. the beverage dispensing device of claim 1 wherein the internal passage of the nozzle comprises at least two vertical passages.

18. The beverage dispensing apparatus of claim 17 wherein the internal passage of the nozzle comprises four vertical passages.

19. A beverage dispensing system comprising:

a container for carbonated beverage;

an energy source that pressurizes the carbonated beverage in the container;

a valve in fluid communication with the beverage in the container, the valve having an open position and a closed position;

a spout having: a liquid receiving end in fluid communication with the valve; an internal passage through which the carbonated beverage flows in cross-section when the valve is in an open position; a liquid dispensing end having an opening through which said carbonated beverage exits into an ambient environment at least initially, wherein said cross-section of said internal passageway of said spout decreases from said liquid receiving end to said liquid dispensing end of said spout such that carbonated beverage flowing through said spout substantially continuously contacts a surface of said internal passageway from said liquid receiving end to said liquid dispensing end.

20. The beverage dispensing system of claim 19 wherein the reduction in the cross-sectional area of the internal passageway of the nozzle is continuous.

21. The beverage dispensing system of claim 20 wherein the cross-sectional profile of the internal passage approximates the cross-sectional profile of a free-falling stream of liquid at ambient pressure.

22. The nozzle of claim 19 including a liquid dispersion member having a liquid receiving end and a liquid dispensing end.

23. The beverage dispensing system of claim 22 wherein the liquid dispersion member is removably supported in the liquid dispensing region of the internal passage of the nozzle.

24. The beverage dispensing system of claim 23 wherein the liquid dispersion member is substantially stationary.

25. The beverage dispensing system of claim 22 wherein the beverage dispersing member further comprises a liquid dispersing surface that is generally an inverted cone.

26. The beverage dispensing system of claim 25 wherein the beverage dispersing surface of the beverage dispersing member extends from the liquid dispensing opening of the nozzle.

27. The beverage dispensing system of claim 26 wherein the liquid dispersing surface of the liquid dispersion member extends from the liquid dispensing end of the nozzle from about 0.2 inches to about 1.5 inches.

28. The beverage dispensing system of claim 24 wherein the liquid dispersion member is adjustable.

29. The liquid dispersion member of claim 25 wherein the liquid dispersion surface has a gradually decreasing slope.

30. The liquid dispersion member of claim 29 wherein the liquid dispersion surface disperses liquid from the nozzle at an angle relative to a longitudinal axis of the nozzle.

31. The liquid dispersion member of claim 30 wherein the liquid dispersion surface disperses liquid from the nozzle substantially perpendicular to the axis of the nozzle.

32. The liquid dispersion member of claim 30 wherein the dispersion surface disperses liquid radially from the liquid dispersion member.

33. The beverage dispensing system of claim 19 wherein the nozzle further comprises at least two vertical channels.

34. The beverage dispensing system of claim 33, wherein the valve comprises a valve head, a valve stem, and a valve body.

35. The valve of claim 34, wherein the valve body further comprises a valve shoulder biased against the valve stem.

36. The valve of claim 35, wherein the surface of the valve shoulder conforms to the inner contour of the valve housing.

37. The valve of claim 36, wherein a portion of the shoulder surface forms an acute angle with the axis of the stem.

38. The valve of claim 37, wherein the surface of the valve shoulder is concave.

39. A beverage dispensing apparatus comprising:

a pipe orifice;

a valve means;

and a diffuser located upstream of the valve arrangement, the diffuser having a first end, a second end, and an internal passage between the first end and the second end;

wherein a cross-section of the internal passage of the diffuser increases from the first end to the second end.

40. The beverage dispensing apparatus of claim 39 wherein the angle of divergence from the axis of the diffuser to the surface of the internal passage is less than 25 degrees.

41. The beverage dispensing device of claim 40 wherein the spread angle is 12 degrees or less.

42. The beverage dispensing device of claim 41 wherein the spread angle is 8 degrees or less.

43. A beverage dispensing apparatus, comprising:

means for introducing a beverage to be dispensed into said beverage dispensing means;

means for increasing the flow rate of the liquid in the apparatus;

means for reducing turbulence in the liquid flow;

means for reducing foam in the liquid dispensed from the device;

and means for controlling the dispensing of liquid from the device.

44. The beverage dispensing apparatus of claim 43 further comprising means for reducing pressure.

45. The beverage dispensing device of claim 44 further comprising means for cooling liquid in the beverage dispensing device.

46. The beverage dispensing device of claim 45 further comprising means for selectively controlling the flow rate of liquid through the beverage dispensing device.

47. A beverage dispensing apparatus comprising:

a container for carbonated beverage;

an energy source that pressurizes the carbonated beverage in the container;

a valve in fluid communication with the beverage in the container, the valve having an open position and a closed position, the valve having a valve housing, a valve seat and a valve head, the valve housing having an inlet and an outlet and a curved interior surface forming a curved flow chamber, and a valve shoulder having a liquid facing surface, wherein the liquid facing surface is shaped to match the curvature of the interior surface of the valve housing.

48. The beverage dispensing apparatus of claim 47 wherein the liquid-facing surface is generally in the shape of a portion of an arcuate cylinder.

49. The beverage dispensing apparatus of claim 48 wherein the liquid facing surface is generally concave and has two radii of curvature.

50. The beverage dispensing apparatus of claim 47 wherein the valve head is generally oval-shaped.

51. The beverage dispensing apparatus of claim 47 wherein the valve head is generally spherical.

52. A beverage dispensing apparatus as claimed in claim 47, wherein the valve head opens in the direction of the valve housing inlet.

53. The beverage dispensing apparatus of claim 1 including means for selectively reducing the pressure of the liquid upstream of the nozzle.

54. The beverage dispensing apparatus of claim 53 wherein the means for selectively reducing the pressure of the liquid upstream of the nozzle comprises a multi-way valve.

55. The beverage dispensing apparatus of claim 54 wherein the means for selectively reducing the pressure of liquid upstream of the nozzle comprises a length of beverage tubing.

56. The beverage dispensing apparatus of claim 53 wherein the means for selectively reducing the pressure of the liquid upstream of the nozzle comprises a multi-way valve and a length of beverage tubing, wherein the multi-way valve is capable of selectively directing the liquid to flow through or around the length of beverage tubing.

57. A method of reducing foam formation in a carbonated beverage comprising:

directing the flow of liquid to a liquid dispensing nozzle, the liquid dispensing nozzle comprising: a flow control valve having an open position and a closed position, a liquid receiving opening, a liquid dispensing opening, and a reduced cross-sectional area flow path;

placing the bottom of the interior of the liquid receiving container adjacent the opening of the spout;

moving the valve to the open position to allow liquid to flow through the orifice;

directing liquid flowing through the spout to the liquid dispensing opening along a path generally parallel to the spout; and is

Redirecting the flow of liquid in a direction substantially tangential to the liquid receiving vessel with a liquid flow diverter at the spout opening.