WO2007018605A1 - Diffuseur d'entree pour un condenseur - Google Patents

Diffuseur d'entree pour un condenseur Download PDF

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Publication number
WO2007018605A1
WO2007018605A1 PCT/US2006/008203 US2006008203W WO2007018605A1 WO 2007018605 A1 WO2007018605 A1 WO 2007018605A1 US 2006008203 W US2006008203 W US 2006008203W WO 2007018605 A1 WO2007018605 A1 WO 2007018605A1
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WO
WIPO (PCT)
Prior art keywords
chamber
condenser
refrigerant
inlet
flow
Prior art date
Application number
PCT/US2006/008203
Other languages
English (en)
Inventor
Jun Wang
Mahesh Valiya Naduvath
John F. Judge
Original Assignee
York International Corporation
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by York International Corporation filed Critical York International Corporation
Publication of WO2007018605A1 publication Critical patent/WO2007018605A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/046—Condensers with refrigerant heat exchange tubes positioned inside or around a vessel containing water or pcm to cool the refrigerant gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/007—Condensers

Definitions

  • the present invention is directed to a refrigerant flow control and pressure recovery device for use with vapor compression refrigeration systems in HVAC applications, and more particularly, is directed to a refrigerant pressure recovery device for use with shell and tube type condensers, where cooling fluids such as water flows through tubes and the refrigerant flows through the shell and is cooled and condensed on the outside surface of the tubes.
  • Condensers are an important component used in vapor compression refrigeration systems in HVAC applications.
  • refrigerant vapor enters the shell of the condenser and flows across the outside surface of a plurality of cooling tubes.
  • Each of the tubes contains a cooling fluid (e.g., water) at a lower temperature circulating inside these tubes.
  • a cooling fluid e.g., water
  • heat transfer occurs from the refrigerant to the lower temperature fluid circulating inside the tubes, such that refrigerant temperature lowers below the saturation temperature and condenses on the outside of the tubes.
  • the condensed refrigerant exits the condenser in the liquid state and the warmer fluid circulating inside the tubes is typically directed to a cooling tower.
  • the condensed liquid refrigerant from the condenser flows through an expansion device to an evaporator.
  • the two-phase refrigerant in the evaporator enters into a heat exchange relationship with a secondary fluid to lower the temperature of the secondary fluid that is circulated to regulate the temperature of an area inside a structure.
  • the refrigerant liquid in the evaporator undergoes a phase change to a refrigerant vapor as a result of the heat exchange relationship with the secondary liquid and is returned to the compressor where the pressure of the refrigerant vapor is elevated and discharged into the condenser to complete the cycle.
  • the refrigerant vapor from the discharge of a compressor enters the shell of the condenser at relatively high velocity.
  • An impingement baffle is typically disposed on the inlet of a shell side condenser to prevent direct impingement of the high velocity refrigerant vapor on the condenser tubes. This direct impingement can cause damage to the condenser tubes, such as by vibration, pitting and erosion.
  • Conventional impingement baffles define an elongate, narrow chamber that directs the incoming refrigerant vapor toward opposed ends of the condenser.
  • the impingement baffle While preventing damage to the condenser tubes, the impingement baffle causes a drop in pressure of the incoming refrigerant vapor as compared to the pressure of the refrigerant vapor at the compressor outlet.
  • the compressor needs to compress the refrigerant vapor to a higher pressure to make up this pressure drop with more power consumption, thereby lowering the overall refrigeration system efficiency.
  • Liquid hump refers to a rise in the level of the condensed refrigerant liquid in the central portion of the condenser shell as compared to the level at the ends of the condenser shell thereby reducing the effective heat transfer surface area, which can reduce condenser efficiency.
  • the high velocity refrigerant causes undesirable splashing of the liquid refrigerant in the condenser shell.
  • the condensing saturation pressure and temperature inside the shell is higher when using the diffuser of the present invention due to static pressure recovery. Without altering the temperature of the fluid circulating through the condenser tubes to cool the refrigerant, the temperature difference between the two is increased, so that less heat transfer surface is needed to reject the same amount of heat.
  • Using the diffuser of the present invention provides opportunity to use a smaller condenser to achieve the same system efficiency.
  • the present invention relates to a diffuser situated at the inlet of a shell side condenser of a vapor compression refrigeration system.
  • the diffuser includes an inlet to receive a compressed refrigerant vapor from a compressor of the vapor compression refrigeration system.
  • a chamber is in fluid communication with the inlet to receive compressed refrigerant vapor.
  • the chamber has an upper side, a lower side and lateral sides bridging the upper and lower sides.
  • the chamber also has a plurality of openings to discharge refrigerant vapor inside the condenser shell.
  • a protrusion is disposed inside the chamber.
  • the protrusion and the chamber are configured and disposed to diffuse and direct a flow of refrigerant from the discharge of the compressor to inside the condenser.
  • the refrigerant leaving the chamber of the diffuser has a higher pressure than the refrigerant entering the diffuser at the inlet of the condenser.
  • the inlet of the diffuser typically is in very close proximity to the compressor discharge
  • the present invention further relates to a chiller system including a compressor, a condenser arrangement and an evaporator arrangement connected in a closed refrigerant loop.
  • An inlet is in fluid communication between the compressor and the condenser arrangement to receive a compressed refrigerant vapor from the compressor.
  • a chamber is in fluid communication with the inlet to receive compressed refrigerant.
  • the chamber has an upper side, a lower side and lateral sides bridging the upper and lower sides.
  • the chamber also has a plurality of openings to discharge refrigerant inside the condenser arrangement.
  • a protrusion is disposed inside the chamber.
  • the protrusion and the chamber are configured and disposed to diffuse and direct a flow of refrigerant from the discharge of the compressor to inside the condenser.
  • the refrigerant leaving the chamber has a higher pressure than the refrigerant entering the chamber at the inlet of the condenser.
  • the inlet of the condenser typically is in very close proximity to the compressor discharge.
  • the present invention still further relates to a condenser including an inlet to receive a compressed refrigerant from a compressor of a vapor compression refrigeration system.
  • a chamber is in fluid communication with the inlet to receive compressed refrigerant.
  • the chamber has an upper side, a lower side and lateral sides bridging the upper and lower sides.
  • the chamber also has a plurality of openings to discharge refrigerant inside the condenser.
  • a protrusion is disposed inside the chamber.
  • the protrusion and the chamber are configured and disposed to diffuse and direct a flow of refrigerant from the discharge of the compressor to inside the condenser.
  • the refrigerant leaving the chamber has a higher pressure than the refrigerant entering the chamber at the inlet of the condenser.
  • the inlet of the condenser typically is in very close proximity to the compressor discharge.
  • An advantage of the present invention is that it facilitates static pressure recovery of the refrigerant entering the condenser, thereby increasing the pressure of the refrigerant vapor leaving the diffuser compared to the pressure of refrigerant entering the diffuser
  • An advantage of the present invention is that it increases vapor compression refrigeration system efficiency.
  • a further advantage of the present invention is that it reduces tube vibration associated with operation of the condenser.
  • a yet additional advantage of the present invention is that it reduces the level of liquid hump inside the condenser.
  • FIG. 1 is a schematic showing a refrigeration system using a condenser inlet diffuser of the present invention.
  • FIG. 2 is an elevation view of a condenser having a condenser inlet diffuser of the present invention.
  • Fig. 3 is a partial cross section of the condenser and condenser inlet diffuser taken along line 3-3 of Fig. 2 of the present invention.
  • FIG. 4 is a perspective view of an embodiment of a condenser inlet diffuser of the present invention.
  • FIGs. 5 and 6 are top views of the condenser inlet diffuser shown in Fig. 4 of the present invention.
  • Fig. 7 shows overlaid cross sections of the condenser inlet diffuser taken along lines A-A and B-B of Fig. 6 of the present invention.
  • Fig. 8 is a graph comparing pressure recovery of the refrigerant vapor exiting the compressor and entering the condenser between refrigeration systems with and without an inlet diffuser of the present invention.
  • Fig. 9 is a graph that shows the gain (or difference) in the saturation temperature of the refrigerant in the condenser corresponding to the increase in pressure of the refrigerant exiting the compressor and entering the condenser.
  • Fig. 10 is a perspective view of an alternate embodiment of a condenser inlet diffuser of the present invention.
  • Figure 11 is an end view of a condenser inlet diffuser of Fig. 10 of the present invention.
  • Figure 12 is a partial cross section of the condenser and condenser inlet diffuser taken along line 3-3 of Fig. 2 of the present invention.
  • FIG. 1 One embodiment of a refrigeration system 100 using a shell side condenser inlet diffuser 114 of the present invention is shown in Figure 1.
  • the refrigeration system 100 preferably receives electrical power from an AC power source 102 that drives a drive unit 104, such as a variable speed drive or VSD.
  • Drive unit 104 which is controlled by a control panel 108, drives a motor 106 that likewise drives a compressor 110.
  • Compressor 110 compresses a refrigerant vapor and delivers the vapor to the condenser 112 through a discharge line.
  • the compressor 110 can be any suitable type of compressor, e.g., screw compressor, centrifugal compressor, reciprocating compressor, scroll compressor, etc.
  • the refrigerant vapor delivered by the compressor 110 to the condenser 112 first passes through a diffuser 114, which is discussed in further detail below.
  • the refrigerant vapor Upon entering condenser 112, the refrigerant vapor enters into a heat exchange relationship with a fluid, typically water that is circulated via tubes disposed inside the condenser.
  • a fluid typically water that is circulated via tubes disposed inside the condenser.
  • This condenser configuration is referred to as a shell and tube condenser, with refrigerant condensing on the outside of the tubes and the fluid (e.g., water) flowing inside of the tubes.
  • the refrigerant vapor undergoes a phase change to a refrigerant liquid as a result of the heat exchange relationship with the fluid.
  • the evaporator 116 can include connections for a supply line and a return line of a cooling load.
  • a secondary liquid e.g., water, ethylene or propylene glycol, calcium chloride brine or sodium chloride brine, travels into the evaporator 116 via return line and exits the evaporator 116 via supply line.
  • the liquid refrigerant in the evaporator 116 enters into a heat exchange relationship with the secondary liquid to lower the temperature of the secondary liquid.
  • the refrigerant liquid in the evaporator 116 undergoes a phase change to refrigerant vapor as a result of the heat exchange relationship with the secondary liquid.
  • the vapor refrigerant in the evaporator 116 exits the evaporator 116 and returns to the compressor 110 by a suction line to complete the cycle.
  • the diffuser 114 is applied to shell side condensers of shell and tube type 112 where the refrigerant condenses on the outside of the tubes (shell side) whereas the evaporator 116 used in the system 100 can be of any suitable configuration, provided that the appropriate phase change of the refrigerant in the condenser 112 and evaporator 116 is obtained.
  • the refrigeration or liquid chiller system 100 can include many other features that are not shown in Figure 1. These features have been purposely omitted to simplify the drawing for ease of illustration.
  • condenser 112 has an embodiment of an inlet diffuser 114 of the present invention.
  • An inlet pipe 127 connected to the diffuser 114 extends through an upper portion of a shell 113 of condenser 112.
  • the inlet pipe 127 is secured to the shell 113, such as by welding, or any other suitable means.
  • the inlet pipe 127 also has the appropriate thickness to permit welding to the shell.
  • a flange 130 is At the end of the inlet pipe 127 opposite the diffuser 114 and exterior of the shell 113 of condenser 112 for connecting the inlet pipe 127 to a corresponding pipe to receive pressurized refrigerant vapor from the compressor 110 (Fig 1).
  • Flared portion 132 helps transition the substantially vertical direction of flow of refrigerant vapor flowing into the condenser 1 12 along the inlet pipe 127 to flow substantially horizontally upon exiting the diffuser 114.
  • the radius of curvature of flared portion 132 is sized and configured, primarily based on the flow rate of refrigerant and the size of inlet pipe 127, to provide a smooth transition of refrigerant flow which minimizes a swirling or twisting component with respect to the desired direction of flow.
  • a support frame 118 can be used to secure the inlet pipe 127 supporting the diffuser 114.
  • flared portion 132 which extends inside the shell 113 of the condenser 112, transitions along a tangency curve 134 to an upper surface 136.
  • the tangency curve 134 does not necessarily define a circle, nor is the upper surface 136 necessarily planar, as in an alternate embodiment (Fig. 12), upper surface 136 could be coincident with the condenser shell 113, or in a further alternate embodiment, the upper surface 136 could actually be the condenser shell 113.
  • Upper surface 136 defines a pair of lobes 138, 140.
  • Lobe 138 is defined by edges 146, 148 and 150
  • lobe 140 is defined by edges 152, 154 and 156.
  • One end of edge 146 is defined by a juncture 142 which is the juncture between edges 146 and edge 152, and preferably, also coincides with the tangency curve 134.
  • the other end of edge 146 is defined by a juncture 168 between edge 146 and edge 150.
  • edges 146, 148 each define outwardly directed curves, or convex profiles with regard to lobe 138, although edges 146, 148 can define non-convex profiles, including linear profiles.
  • edges 146, 148 having convex profiles or suitable non-convex profiles, it can be shown that any line drawn parallel to a reference line 182 connecting junctures 142, 144 along upper surface 138 between junctures 168, 170 is longer than reference line 182.
  • the reference line 182 is substantially transverse to the length of the condenser 112.
  • the diffuser 114 is preferably bifurcating the flow of refrigerant vapor entering the diffuser 114 along the inlet pipe 127. Stated another way, the distance between corresponding points along edges 146, 148 parallel to reference line 182 increases as the distance of the parallel lines from the reference line 182, i.e., the parallel lines moving along lobe 138 toward edge 150, increases.
  • edge 150 Adjacent to edges 146 and 148 and defined by respective junctures 168, 170 is edge 150.
  • Edge 150 is preferably outwardly directed or convex with respect to upper surface 138.
  • the curvature of edge 150 is substantially radial, with the center of curvature being coincident with the center of a projection 176.
  • the curvature of edge 150 can also be elliptical.
  • lobe 140 is defined by edges 152, 154 and 156, while lobe 138 is defined by edges 146, 148 and 150.
  • One end of edge 152 is defined by a juncture 142 which is the juncture between edges 146 and edge 152, and preferably, also coincides with the tangency curve 134.
  • the other end of edge 152 is defined by a juncture 172 between edge 152 and edge 156.
  • edges 152, 154 each define outwardly directed curves, or convex profiles with regard to lobe 140, although edges 152, 154 can define non-convex profiles, including linear profiles.
  • edges 152, 154 having convex profiles or suitable non-convex profiles, it can be shown that any line drawn parallel to a reference line 182 connecting junctures 142, 144 along lobe 140 and between junctures 172, 174 is longer than reference line 182. Stated another way, the distance between corresponding points along edges 152, 154 parallel to reference line 182 increases as the distance of the parallel lines from the reference line 182, i.e., the parallel lines moving along lobe 140 toward edge 156, increases. [0034] Adjacent to edges 152 and 154 and defined by respective junctures 172, 174 is edge 156. Edge 156 is preferably outwardly directed or convex with respect to lobe 140. Preferably, the curvature of edge 156 is substantially radial, with the center of curvature being coincident with the center of projection 176. However, the curvature of edge 156 can also be elliptical.
  • lobes 138, 140 are symmetrical to each other about the reference line 182 that is preferably coincident with the apex of the protrusion 176, lobes 138, 140 may have a different line of symmetry, lack a line of symmetry, or be asymmetric to each other.
  • a lower surface 158 is substantially similar in size and shape as upper surface 136, with lower surface 158 and upper surface 136 being separated by a distance 184 that is configured to yield the most favorable results, primarily based on the refrigerant flow rate.
  • Protrusion 176 preferably extends upwardly from the lower surface 158 to help smoothly transition substantially vertically directed refrigerant vapor flow to substantially horizontally directed refrigerant vapor flow upon leaving the diffuser 114.
  • protrusion 176 is a right circular cone, with the apex of the cone disposed coincident with the center of the neck 128 of the inlet pipe 127.
  • protrusion geometries can also be used.
  • protrusion 176 is affixed to the lower surface 158, the protrusion 176 can also be positioned using any suitable mounting arrangement in the refrigerant vapor flow stream between the upper surface 136 and the lower surface 158, or if the protrusion is large enough in at least one direction, to be positioned between the lower surface 158 and the inlet tube 127.
  • lateral surfaces 160, 162, 164, 166 Extending between and bridging the upper and lower surfaces 136, 158 are lateral surfaces 160, 162, 164, 166.
  • lateral surface 160 bridges the upper and lower surfaces 136, 158 between juncture 142 and juncture 168 and lateral surface 164 bridges the upper and lower surfaces 136, 158 between juncture 142 and juncture 172.
  • lateral surface 162 bridges the upper and lower surfaces 136, 158 between juncture 144 and juncture 170 and lateral surface 166 bridges the upper and lower surfaces 136, 158 between juncture 144 and juncture 174.
  • refrigerant vapor that is directed inside the inlet pipe 127, through the flared portion 132, then between the upper and lower surfaces 136, 158 is substantially constrained to flow through an opening 186 between corresponding edges 150 of the upper and lower surfaces 136, 158 in one direction, and an opening 188 between corresponding edges 156 of the upper and lower surfaces 136, 158 in the other direction.
  • lower surface 158 is added having substantially identical edges 146, 148, 152, 154 and a pair of vertical planes that are parallel to the reference line 182 coincident with line A-A and with line B-B.
  • Each of the corners of the cross section cut by the plane coincident with line A-A through the upper and lower surfaces 136, 158 is labeled as "A”
  • each of the corners of the cross section cut by the plane coincident with line B-B through the upper and lower surfaces 136, 158 is labeled as "B”.
  • Fig. 5 only included the upper surface 136
  • Fig. 6 includes both upper and lower surfaces 136, 158 and lateral surfaces 146, 162. Therefore, the vertically oriented plane that is coincident with line A-A cutting through the upper and lower surfaces 136, 158 of diffuser 114 defines a cross sectional area defining A-A-A-A. Similarly, the vertically oriented plane that is coincident with line B-B cutting through the upper and lower surfaces 136, 158 of diffuser 114 defines a cross sectional area defining B-B-B-B. As shown in Fig. 7, although not drawn to scale, the area defining B-B-B-B is larger than A-A-A-A.
  • the cross sectional area defined by the intersection of a transverse plane with the upper and lower surfaces 136, 158 and lateral sides 160, 162, 164, 166 of the diffuser 114 continually increases as the distance between the transverse plane and the reference line 182 increases.
  • the refrigerant vapor is then additionally constrained to flow inside the upper and lower surfaces 136, 158 and lateral surfaces 160, 162, 164, 166 toward the opposed ends 150, 156, the cross sectional area defined by these surfaces increasing as the refrigerant vapor flows toward the opposed ends 150, 156.
  • the vapor refrigerant flow is advantageously conditioned and controlled. That is, the flow of refrigerant vapor is turned substantially 90 degrees while keeping flow losses at a minimum.
  • Equation 1 Equation 1
  • C P ⁇ P/ (p/2)(U 0 ) 2 [3] [0045] where Cp is a pressure recovery coefficient, ⁇ P is the absolute pressure recovery or the static pressure difference between the pressure at the inlet of the diffuser and the pressure at the outlet of the diffuser, and the remaining (p/2)(U 0 ) 2 term is the total velocity head at the outlet of the compressor.
  • the pressure recovery coefficient is a parameter frequently used to measure the operating performance of the diffuser.
  • the pressure recovery coefficient is a measure of the amount of the total available velocity head at the inlet of the diffuser that is converted into static pressure.
  • the condenser inlet diffuser of the present invention not only changes the direction of flow of refrigerant vapor from a substantially vertical direction to a substantially horizontal direction with minimal flow losses, but additionally converts a portion of the kinetic energy component to a pressure head or static pressure component as shown in equation 1. That is, the condenser inlet diffuser reduces the velocity of the incoming refrigerant vapor as the refrigerant vapor flows through the inlet diffuser toward the condenser tubes while simultaneously increasing the level of static pressure.
  • the condenser By increasing the level of static pressure, the condenser can operate at an elevated saturation temperature, thereby requiring less heat transfer surface to exchange the same amount of heat, due to higher temperature difference between the refrigerant vapor entering the condenser shell and the fluid flowing through tubes inside the condenser shell. Additionally, by reducing the velocity of the refrigerant vapor, the difference in levels of collected liquid refrigerant along a lower portion of the condenser is substantially equalized, i.e., liquid hump is minimized. Further, direct impingement of tubes of the condenser due to the flow of the refrigerant vapor is minimized.
  • FIG. 8 shows the difference in pressure between the outlet and the inlet of the diffuser and in the conventional impingement baffle arrangement.
  • the abscissa shows the velocity head based on the vertical component of the velocity through the inlet pipe. The value of the abscissa increases from left to right and corresponds to increasing flow into the condenser.
  • the tests were first performed with the condenser inlet having a conventional impingement baffle arrangement, the same tests being performed after the condenser inlet was retrofitted with an inlet diffuser construction similar to Fig. 4. As shown by Fig. 8, pressure recovery occurs in the diffuser and further includes a smooth deceleration of the flow with little loss of energy.
  • Fig. 9 shows the overall saturation temperature gain achieved by the inlet diffuser construction as compared to the conventional impingement baffle arrangement.
  • Figs. 10 and 11 is an alternate embodiment of the inlet diffuser 214 in which the tangency curve 134 is substantially flush with the condenser shell 113 so that the condenser shell 113 defines the upper surface 136 of the inlet diffuser 214.
  • the tangency curve 134 is substantially flush with the condenser shell 113 so that the condenser shell 113 defines the upper surface 136 of the inlet diffuser 214.

Abstract

L'invention concerne un diffuseur d'entrée (114) pour un condenseur du côté de l'enveloppe extérieure, pour un système de réfrigération par compression de vapeur. Le diffuseur (114) comporte une entrée (127) servant à recevoir du réfrigérant comprimé provenant d'un compresseur d'un système de réfrigérant. Une chambre est en communication fluidique avec l'entrée (127) pour recevoir du réfrigérant comprimé, la chambre ayant un côté supérieur et un côté inférieur et des côtés latéraux reliant les côtés supérieur et inférieur, la chambre ayant une pluralité d'ouvertures (186, 188) permettant de décharger le réfrigérant à l'intérieur du condenseur (112). Une saillie (176) est disposée à l'intérieur de la chambre. La saillie (176) et la chambre sont configurées et disposées de manière à diffuser et diriger un écoulement de réfrigérant du compresseur vers l'intérieur du condenseur (112), le réfrigérant quittant la chambre ayant un niveau de pression supérieur au réfrigérant entrant dans la chambre.
PCT/US2006/008203 2005-08-04 2006-03-08 Diffuseur d'entree pour un condenseur WO2007018605A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US11/197,564 US20070028647A1 (en) 2005-08-04 2005-08-04 Condenser inlet diffuser
US11/197,564 2005-08-04

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WO2007018605A1 true WO2007018605A1 (fr) 2007-02-15

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WO2020020349A1 (fr) * 2018-07-27 2020-01-30 约克（无锡）空调冷冻设备有限公司 Condenseur
SG11202100967WA (en) 2018-10-25 2021-03-30 Daicel Corp Tow band for electronic cigarette tip, tip for electronic cigarette, method for manufacturing tow band for electronic cigarette tip, and method for manufacturing electronic cigarette tip
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