US3732029A - Compact heat exchanger - Google Patents

Compact heat exchanger Download PDF

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Publication number
US3732029A
US3732029A US00207924A US3732029DA US3732029A US 3732029 A US3732029 A US 3732029A US 00207924 A US00207924 A US 00207924A US 3732029D A US3732029D A US 3732029DA US 3732029 A US3732029 A US 3732029A
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US
United States
Prior art keywords
shaft
heat exchanger
holes
passageways
header
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
US00207924A
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English (en)
Inventor
J Raymond
C Thomson
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CBS Corp
Original Assignee
Westinghouse Electric Corp
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Filing date
Publication date
Application filed by Westinghouse Electric Corp filed Critical Westinghouse Electric Corp
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Publication of US3732029A publication Critical patent/US3732029A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/047—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/586—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps
    • F04D29/588—Cooling; Heating; Diminishing heat transfer specially adapted for liquid pumps cooling or heating the machine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D7/00—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts
    • F04D7/02—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type
    • F04D7/06—Pumps adapted for handling specific fluids, e.g. by selection of specific materials for pumps or pump parts of centrifugal type the fluids being hot or corrosive, e.g. liquid metals
    • 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
    • F28D7/04—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 spirally coiled

Definitions

  • ABSTRACT The heat transfer efficiency of a heat exchanger is increased by making the entire flow pattern of the exchanger a straight-through flow pattern; thereby providing a compact heat exchanger which is substantially 100 percent effective and compact in size.
  • a prior heat exchanger, or cooler, provided for a prior centrifugal pump had two features, which were I essential for its operation. First, a separator plate was required mid-way in the exchanger to divert the fluid flow. Secondly, a labyrinth seal was required on the separator plate at the shaft of the pump. The cooling operation of the prior exchanger was considerably less than 100 percent effective due to the flow characteristics of the fluid being cooled. Therefore, the prior exchanger could not be compact and still provide the required cooling effect.
  • a centrifugal pump having a shaft rotatably mounted in a generally cylindrical casing is provided with an annular heat exchanger which surrounds the shaft between a first labyrinth seal and a second labyrinth seal .located on the shaft where it passes through a first wall and a second wall. of the exchanger.
  • the fluid to be cooled enters water channels or passageways located at the first labyrinth seal. From the water channels it collects in a first header one wall of which is a disc-like distribution plate having a series of holes therein. The area of the holes is increased as the distance of the holes to the center line of the shaft increases.
  • the fluid passes from the first header through the holes in the plate into the heat exchanger compartment at a uniform flow rate and flows through the compartment with a straight-through flow pattern. After passing over the heat exchanger coils the fluid is collected in a second header constructed in a manner similar to the first header. The cooled fluid flows from the second header through channels located at the second labyrinth seal.
  • FIG. 1 is a view, partly in section and partly in elevation, of a centrifugal pump having a heat exchanger embodying principal features of the invention
  • FIG. 2 is an enlarged view, in plan, of one of the disclike distribution plates utilized in the heat exchanger;
  • FIG. 3 is an enlarged view, in plan, of a modified disc-like distribution plate
  • FIG. 4 is an enlarged view, in section, of a portion of a heat exchanger constructed in accordance with the prior art
  • FIG. 5 is an enlarged view, in section, of a-portion of -the present heat exchanger.
  • FIG. 6 is an enlarged view in plan, of one of the cooling tubes or coils utilized in the heat exchanger.
  • the centrifugal pump 10 shown therein comprises a generally cylindrical casing 11 having a radial discharge nozzle 12 near the upper end of the casing and a suction nozzle 13 at the lower end of the casing, a main annular flange 14 having a generally cylindrical neck 15 extending downwardly inside the casing 11, a rotatable shaft 16 extending through the flange 14 and the neck 15, and an impeller 17 attached to the lower end of the shaft 16 by means of an impeller nut 18 and a bolt 19.
  • the shaft 16 may be driven by an electric motor (not shown) mounted on a motor support stand 21 attached to the top of the main flange 14 by bolts 22.
  • the shaft of the motor is connected to the shaft 16 by means of a coupling 23.
  • the upper end of the casing 11 is attached to the main flange 14 by means of bolts 24 which extend through the flange 14 and are threaded into the casing l 1.
  • a radial bearing assembly 25 for the shaft 16 is attached to the lower end of the neck 15 by means of bolts 26.
  • the bearing assembly 25 may be of any suitable type.
  • the assembly includes a sleeve 27, pressed on the shaft 16, suitable bearing material 28 and a housing 29 enclosing the bearing material 28.
  • breakdown bushings 31 surround the shaft 16 inside the neck 15 above the bearing assembly 25.
  • the bushings 31 may be of a type well known in the art.
  • Shaft seals 30 of a controlled leakage type are disposed in the main flange 14 above the breakdown bushings.
  • the seals 31 are retained in position by a housing 32 attached to the top of the flange 14 by bolts 33.
  • a vapor seal housing 34 is attached to the seal housing 32 by means of bolts 35.
  • a cover 36 for the housing 34 is attached to the housing by means of bolts 37.
  • the shaft seals within the housings 32 and 34 may be of a type well known in the art, such as, for example, the seal arrangement described in US. Pat. No. 3,347,552, issued Oct.
  • a suitable leak-off connection may be made to the housing 32 by means of a coupling 38 and a pipe 39 attached to the housing 32.
  • a leak-off connection may be made to the housing 34 by means of a coupling 41 and a pipe 40 attached to the housing 34.
  • the leak-off liquid is returned to the circulatory system in a manner well known in the art.
  • the present pump is suitable for circulating a liquid in a circulatory system at a relatively high temperature and a high pressure. Suitable connections may be made to the suction nozzle 13 and to the discharge nozzle 12 to enable the pump to circulate the liquid in the system.
  • the pump includes a main impeller seal ring 42, a diffuser 43 extending upwardly from the impeller 17 inside the casing 11 and a guide elbow 44 connecting the diffuser 43 with the radial discharge nozzle 12.
  • the liquid drawn into the pump through the suction nozzle 13 by the impeller 17 is directed to the discharge nozzle 12 by means of the diffuser 43 and the elbow 44.
  • a cylindrical thermal barrier 45 surrounds the bearing as sembly 25, and an annular heat exchanger or cooler 46 is disposed between the impeller 17 and the bearing assembly 25.
  • the cylindrical barrier 45 includes an inner wall 47 and an outer wall 48 spaced from the inner wall 47.
  • the upper ends of the walls 47 and 48 are secured to a thermal barrier flange 49, as by welding.
  • the flange 49 is clamped between the main flange l4 and the casing 11 by means of the flange bolts 24.
  • the lower end of the space between the walls 47 and 48 is closed by an annular bottom wall 51.
  • a flange ring 53 is provided on the outer wall 48.
  • a diffuser 43 is attached to the flange ring 53, as by welding.
  • the guide elbow 44 has upwardly extending support members 54 and 55 which are attached to the flange 49 by means of bolts 56.
  • a cylindrical member 52 extends between the flange 53 and the support members 55.
  • the heat exchanger 46 comprises an annular compartment 57 defined by a first or lower wall 58 surrounding the shaft 16, a second or upper wall 59 surrounding the shaft and spaced along the shaft from the first wall, an inner sleeve 61, and an outer sleeve 62 radially spaced from the inner sleeve.
  • the sleeves 61 and 62 extend parallel to the shaft between the first wall 58 and the second wall 59.
  • a plurality of cooling coils or tubes 63 are disposed within the compartment 57.
  • a first header 64 in the first wall 58 is provided with a disc-like distribution plate 65 having a series of holes 66 therein.
  • a second header 67 in the second wall 59 is provided with a disc-like distribution plate 65 similar to the plate in the first header to permit a uniform flow of fluid out of the compartment 57.
  • the holes 66 in each plate 65 are located in a plurality, for example, three circular rows spaced radially outwardly from the center of the shaft.
  • the number of holes in successive rows increases as the radial distance from the center of the shaft increases.
  • the inner row contains 16 holes
  • the middle row contains holes
  • the outer row contains 24 holes, all of the same diameter.
  • the number of holes 66a in each row is the same, but the diameter of the holes in successive rows increases as the radial distance from the center line of the shaft increases. Accordingly, the area of the holes in the modified plates increases as the distance to the center line of the shaft increases.
  • a first labyrinth seal 68 is provided on the shaft 16 where the first wall 58 encircles the shaft.
  • a second labyrinth seal 69 is provided on the shaft where the second wall 59 encircles the shaft.
  • the first wall 58 has a plurality of passageways 71 therein extending from the first header 64 to the shaft 16 at the first seal means 68.
  • the second wall 59 has a plurality of passageways 72 therein extending from the second header 67 to the shaft at the second seal means 69.
  • relatively small openings 73 and 74 are provided in the impeller 17 to admit liquid into a chamber 75 above the impeller.
  • a relatively small amount of the liquid being circulated by the impeller is caused to flow through a portion of the first labyrinth seal 68 and the first passageways 71 into the first header 64.
  • the liquid flows from the header 64 through the holes 66 in the first distribution plate 65 into the heat exchanger compartment 57 at a uniform flow rate over the area of the compartment.
  • the liquid flows through the compartment over the cooling tubes 63 with a straightthrough flow pattern.
  • the cooled liquid is permitted to flow out of the compartment through the holes 66 in the second distribution plate 65 into the second header 67, thence through the second passageways 72 and a portion of the second labyrinth seal 69 along the shaft 16 into the area around the bearing assembly 25.
  • the first labyrinth seal 68 directs the liquid into the first passageways 71 and the second labyrinth seal 69 directs the liquid along the shaft into the area around the bearing assembly.
  • a cooling liquid such as water
  • passageways 76 and 77 in the flange 49 communicate with pipes 78 and 79, respectively. These pipes pass through the space between the neck 15 and a cylindrical wall 81 which extends between the flange 49 and the second or upper wall 59 of the heat exchanger.
  • the pipe 78 communicates with a semicylindrical header 82 which extends along the heat exchanger 46 outside of the outer sleeve 62 of the exchanger.
  • One side of the header 82 is closed by a wall 83 which extends between the first wall 58 and the second wall 59 of the exchanger.
  • the bottom of the header is closed by a wall or plate 84.
  • the pipe 79 communicates with a header 85 (FIG. 6) constructed in a manner similar to the header 82.
  • the passageway 76 may be connected to a suitable supply source by means of a pipe 86.
  • a discharge pipe 87 is connected to the passageway 77.
  • the coils or tubes 63 communicate with the headers 82 and 85, thereby causing the cooling liquid to circulate through the tubes as it flows from the header 82 into the header 85 from which it is discharged through the pipes 79 and 87.
  • the coils or tubes 63 are of a pancake type with spacers 88 disposed between the turns of each coil.
  • the thermal barrier 45 is filled with liquid which is cooled somewhat by the liquid flowing through the pipes 78, 79 the headers 82, 85 and by the liquid in the area around bearing assembly 25.
  • the effectiveness of the thermal barrier 45 may be increased by providing a plurality of spaced concentric sleeves 91 between the inner wall 47 and the outer wall 48.
  • the sleeves 91 separate the liquid inside the thermal barrier into vertical layers, thereby increasing the effectiveness of the thermal barrier.
  • FIGS. and 5 The advantages of the present heat exchanger over prior exchangers may be seen by referring to FIGS. and 5.
  • a separator plate 92 is provided midway in the exchanger to divert the fluid flow.
  • a liquid flowing through the exchanger channels in a manner to decrease the effective heat transfer area which is shown between dot-dash lines.
  • the prior exchanger is considerably less than 100 percent effective due to the flow characteristics and, therefore cannot be compact.
  • a labyrinth seal 93 is required on the separator plate 92 where it encircles the shaft, thereby increasing the cost of the exchanger.
  • the liquid enters the'exchanger compartment 57 at a uniform flow rate over the area of the compartment and flows through the compartment with a straight-through flow pattern.
  • the effective heat transfer area which encompasses all turns of the coils or tubes 63, is greatly increased as compared with the exchanger in FIG. 4. Therefore, the present exchanger can be more compact and requires less space for installation inside the casing of a centrifugal pump.
  • the invention provides a heat exchanger which is highly effective in its cooling operation. Therefore, it is compact in structure and is particularly suitable for installation inside a compact shaft seal casing for a centrifugal pump.
  • An annular heat exchanger for use with a centrifugal pump having an impeller driven by a shaft rotatably mounted in a generally cylindrical casing, comprising first and second seal means spaced along the shaft inside the casing, an annular compartment defined by a first wall surrounding the shaft, a second wall surround ing the shaft and spaced along the shaft from the first wall, at least one cooling tube disposed within the compartment, a first header in the first wall with a disc-like distribution plate having a series of holes therein, the area of the holes increasing as the distance to the center line of the shaft increases, a second header in the second wall similar to the first header, said first wall having first passageways therein extending from the first header to the shaft at said first seal means, said second wall having second passageways therein extending from the second header to the shaft at said second seal means, means causing part of the fluid circulated by the impeller to flow into the exchanger compartment through said first passageways and said first header at a uniform flow rate, and said second header permitting the fluid to flow out of the compartment
  • each disc-like distribution plate located in a plurality of circular rows spaced radially outwardly from the center of the shaft and the number of holes in successive rows increases as the radial distance from the center line of the shaft increases.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00207924A 1971-12-14 1971-12-14 Compact heat exchanger Expired - Lifetime US3732029A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US20792471A 1971-12-14 1971-12-14

Publications (1)

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US3732029A true US3732029A (en) 1973-05-08

Family

ID=22772528

Family Applications (1)

Application Number Title Priority Date Filing Date
US00207924A Expired - Lifetime US3732029A (en) 1971-12-14 1971-12-14 Compact heat exchanger

Country Status (14)

Country Link
US (1) US3732029A (fr)
JP (1) JPS5240058B2 (fr)
AT (1) AT316998B (fr)
BE (1) BE792709A (fr)
CA (1) CA937231A (fr)
CH (1) CH570555A5 (fr)
DE (1) DE2257949C3 (fr)
ES (1) ES408786A1 (fr)
FI (1) FI54648C (fr)
FR (1) FR2165510A5 (fr)
GB (1) GB1365577A (fr)
IT (1) IT971785B (fr)
NL (1) NL7216331A (fr)
NO (1) NO137288C (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4005747A (en) * 1975-06-27 1977-02-01 Borg-Warner Corporation Multi-flow, multi-path heat exchanger for pump-mechanical seal assembly
US4021136A (en) * 1976-02-11 1977-05-03 Westinghouse Electric Corporation Centrifugal pump
US4406465A (en) * 1982-08-13 1983-09-27 A. W. Chesterton Company Centrifugal pump
US4439096A (en) * 1982-08-13 1984-03-27 A. W. Chesterton Company Impeller adjuster for centrifugal pump
US4501530A (en) * 1982-08-13 1985-02-26 A. W. Chesterton Company Centrifugal pump
US4541773A (en) * 1980-06-02 1985-09-17 Jeumont-Schneider Corporation Safety device for motor pump group
US4756665A (en) * 1986-02-03 1988-07-12 Mitsubishi Jukogyo Kabushiki Kaisha Centrifugal compressor
US6644915B2 (en) * 2001-03-12 2003-11-11 Jeumont S.A. Nuclear power station primary pump
CN103573713A (zh) * 2013-02-22 2014-02-12 江苏大学 一种高温自冷却热水循环泵
CN104989673A (zh) * 2015-07-13 2015-10-21 江西省万载水泵有限责任公司 卧式多级离心泵

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51111102U (fr) * 1975-03-03 1976-09-08
US4182413A (en) * 1976-12-23 1980-01-08 General Atomic Company Radial flow heat exchanger
DE4041545A1 (de) * 1990-02-21 1991-08-22 Klein Schanzlin & Becker Ag Kreiselpumpe
FR2756328B1 (fr) * 1996-11-22 1998-12-31 Jeumont Ind Barriere thermique de pompe primaire
ITMI20071685A1 (it) * 2007-08-22 2009-02-23 Luciano Cinotti Reattore nucleare, in particolare reattore nucleare raffreddato a metallo liquido, con scambiatore di calore primario compatto

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2799227A (en) * 1954-07-21 1957-07-16 Westinghouse Electric Corp Thrust bearing
US3459430A (en) * 1967-07-06 1969-08-05 Borg Warner Mechanical seal assembly
US3574473A (en) * 1968-01-24 1971-04-13 Klein Schanzlin & Becker Ag Method and apparatus for cooling parts of pumps in nuclear reactors or the like
US3620639A (en) * 1969-08-22 1971-11-16 Karl Gaffal Pump with hydrostatic bearing
US3652179A (en) * 1971-03-10 1972-03-28 Westinghouse Electric Corp Controlled leakage centrifugal pump
US3666375A (en) * 1969-08-26 1972-05-30 Ernest H Priest Pumping a high or low temperature fluid

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2381777A (en) * 1944-01-29 1945-08-07 Westinghouse Electric Corp Blower apparatus
US2885963A (en) * 1953-12-11 1959-05-12 Hayward Tyler And Company Ltd Structures comprising a motor and a pump driven thereby
CA933802A (en) * 1969-03-25 1973-09-18 Westinghouse Electric Corporation Controlled leakage centrifugal pump

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2799227A (en) * 1954-07-21 1957-07-16 Westinghouse Electric Corp Thrust bearing
US3459430A (en) * 1967-07-06 1969-08-05 Borg Warner Mechanical seal assembly
US3574473A (en) * 1968-01-24 1971-04-13 Klein Schanzlin & Becker Ag Method and apparatus for cooling parts of pumps in nuclear reactors or the like
US3620639A (en) * 1969-08-22 1971-11-16 Karl Gaffal Pump with hydrostatic bearing
US3666375A (en) * 1969-08-26 1972-05-30 Ernest H Priest Pumping a high or low temperature fluid
US3652179A (en) * 1971-03-10 1972-03-28 Westinghouse Electric Corp Controlled leakage centrifugal pump

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4005747A (en) * 1975-06-27 1977-02-01 Borg-Warner Corporation Multi-flow, multi-path heat exchanger for pump-mechanical seal assembly
US4021136A (en) * 1976-02-11 1977-05-03 Westinghouse Electric Corporation Centrifugal pump
US4541773A (en) * 1980-06-02 1985-09-17 Jeumont-Schneider Corporation Safety device for motor pump group
US4406465A (en) * 1982-08-13 1983-09-27 A. W. Chesterton Company Centrifugal pump
US4439096A (en) * 1982-08-13 1984-03-27 A. W. Chesterton Company Impeller adjuster for centrifugal pump
US4501530A (en) * 1982-08-13 1985-02-26 A. W. Chesterton Company Centrifugal pump
US4756665A (en) * 1986-02-03 1988-07-12 Mitsubishi Jukogyo Kabushiki Kaisha Centrifugal compressor
US6644915B2 (en) * 2001-03-12 2003-11-11 Jeumont S.A. Nuclear power station primary pump
CN103573713A (zh) * 2013-02-22 2014-02-12 江苏大学 一种高温自冷却热水循环泵
CN103573713B (zh) * 2013-02-22 2016-08-03 江苏大学 一种高温自冷却热水循环泵
CN104989673A (zh) * 2015-07-13 2015-10-21 江西省万载水泵有限责任公司 卧式多级离心泵
CN104989673B (zh) * 2015-07-13 2018-03-13 江西省万载水泵有限责任公司 卧式多级离心泵

Also Published As

Publication number Publication date
FI54648B (fi) 1978-09-29
BE792709A (fr) 1973-06-14
NO137288B (no) 1977-10-24
CA937231A (en) 1973-11-20
DE2257949C3 (de) 1983-05-19
FI54648C (fi) 1979-01-10
IT971785B (it) 1974-05-10
NL7216331A (fr) 1973-06-18
AT316998B (de) 1974-08-12
DE2257949A1 (de) 1973-06-20
ES408786A1 (es) 1975-10-01
NO137288L (fr) 1973-06-15
JPS5240058B2 (fr) 1977-10-08
CH570555A5 (fr) 1975-12-15
JPS4866255A (fr) 1973-09-11
NO137288C (no) 1978-02-01
GB1365577A (en) 1974-09-04
DE2257949B2 (de) 1980-07-31
FR2165510A5 (fr) 1973-08-03

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