US1951607A - Refrigerator pump - Google Patents
Refrigerator pump Download PDFInfo
- Publication number
- US1951607A US1951607A US604185A US60418532A US1951607A US 1951607 A US1951607 A US 1951607A US 604185 A US604185 A US 604185A US 60418532 A US60418532 A US 60418532A US 1951607 A US1951607 A US 1951607A
- Authority
- US
- United States
- Prior art keywords
- pump
- inlet
- vane
- outlet
- stage
- 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
Links
Images
Classifications
-
- 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
- F25B31/00—Compressor arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C21/00—Oscillating-piston pumps specially adapted for elastic fluids
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2142—Pitmans and connecting rods
Definitions
- This invention relates to oscillating pumps ior handling fluids such as refrigerants and has special reference to a balanced pump capable of high speed operation with mixtures of liquids and I gases without liability-from liquid hammer.
- the piston elements have a harmonic motion similar to that of a pendulum wherein the dual stage of the compression stroke is provided by the decreasing velocity of the piston elements versal point is also subject to accurate initial con trcl which can be maintained in service to provide the minimum possible compression clearance.
- Figure 1 is a side elevation of a pump embodying the features of this invention, together with its driving linkage.
- Figure 2 is an enlarged vertical, longitudinal section thereof taken on the line II-II of Figure 1.
- Figure 3 is an enlarged horizontal section on the line III-IE oi Figure 1.
- Figure 4 showing the pump vane in a different position is a section on the line IV-IV of Figme 2.
- Figure 5 is a section similar to Figure 4.
- Figure 6 is a section showing a modified form of the invention arranged as a two stage pump.
- Figure 7 is a section showing another modiflcaw tion involving foul-stages.
- the general type of pump may conveniently be termed oscillatory as the pumping elements swing back and forth over an arcuate path as 35 distinguished from a completely rotary motion.
- a shaft 10 is oscillated through a fixed angle hy means of a lever 11 and a connecting-rod 12 engaged on crankpins 13, one of which is bolted to a crank disc 14 which may be rotated by any w convenient prime mover, such for example as an electric motor.
- any w convenient prime mover such for example as an electric motor.
- lever 11 is connected to the connecting rod by a second crankpln 13 shown in section in Figure 2, the bearing pin surface 15 thereof being i'rusto-oonical in form and engag- .ing in a complementary bearingsurface 16 in a bushing 17 which is clamped in an aperture in the rod 12 by a nut 18, a spring 19 being interposed between the nut and the end of bearing pin to maintain the some seated in the bushing to 1m necting rod center distance. Since the pump acts in both directions there will be no tendency towards unequal wear which might change the center distance.
- a casing 20 provides a journal 21 for the shaft 10 and a cylindrical recess in one end of the cas ing, concentric with the shaft 10, forms the pump chamber 22, being closed by a cover 23 bolted thereto.
- the other end of the casing is provided 110 with an annular bolted-on flange 24 through which the shaft projects, a diaphragm type of seal 25 being clamped at its periphery between the flange 24 and the casing.
- the diaphragm provides for movement of an inner ring 26 of,
- the shaft 10 carries a concentric hub 29 within the chamber 22, which hub is diametrically slotted to receive a vane 30 which is oscillated within the chamber 22 over a predetermined angle by the linkage previously described.
- Abutment members 31 and 32 are located between the hub 29 and the walls of the chamber 22 and are preferably keyed to the cover as shown at 33 in Figure 3.
- the member 31 in Figures 4 and 5 is on the suction side and is held in place by a cap screw 34 inserted through the suction or inlet connection 35.
- Suction or inlet passages 36 lead from the inlet connection to the compression side of the vane when the ends of the latter swing to the extreme right hand position shownat the top of Figure 5.
- the member 32 is located on the discharge side and is held by another cap screw 34 through the discharge or outlet connection 3'7.
- the discharge abutment contains discharge passages 38 leading therethrcugh to the outlet, these passages containing valve seats 39 for disc valves 40 backed by springs 41 and spring seats 42 threaded into the passages.
- the valve structure must be as light and quick acting as possible with the minimum compression space between the valve and the edge of the abutment against which the vane acts. It the two sides of the pump act in parallel, as in Figures 3, 4 and 5, the discharge passages 38 can be siamese as shown in these figures, while for series or compound action the passages must have separate inlets and outlets as shown in Figures 6 and 7.
- the modification 01. Figure 6 involves a two stage pump differing from that previously described in that individual inlet connections 43 and 44 lead into the upper and lower pumping chambers, and individual outlets are provided at 45 and 46, the inlet 43 being the initial or suction inlet of the first stage, the corresponding outlet 45 being connected to the inlet 44 of the second stage, the outlet 46 of which is the pump delivery connection.
- the inlets are preferably so positioned relative to the vane movements that one inlet is opened as the other closes. This arrangement obviates the need oi an intermediate reservoir between the first stage outlet and the second stage inlet, and both inlets are given the same relative timing to balance the worker the pump.
- Figure '1 discloses a four stage pump wherein each side of each end of the vane delivers a charge during its movement away from the central position shown in the figure.
- the discharge passages 38 are shown as positioned in the cylinder wall although it is to be understood that the previously described outlet abutment structure can be used if desired.
- the connection 4'7 is chosen as the initial inlet
- the corresponding outlet connection 48 delivers to the second stage inlet 49 on the same side but opposite end oi. the vane
- the second stage outlet 50 delivers to the third stage inlet 51 on the opposite side of the same end of the-vane.
- the third stage outlet 52 delivers to the fourth stage inlet 53, the fourth stage outlet 54 being the final pump delivery connection.
- any of the inlets can be chosen for the, initial or suction inlet, in which case the sequence of connections is angularly shifted accordingly for a quadruple compound crank disc 14.
- the vane movement is intended to closely approach the surfaces of the inlet and outlet abutments at the extreme or reversal positions of the vane, the clearances being held to the minimum in the case of a pump intended to handle gasses. Since the shaft 10 holds the vane hub and vane concentric with the cylinder 22, the operating clearances may be set at the very minimum and will not be subject to wear in service as would be the case with reciprocating er rotary eccentric type of pumps.
- An oscillatory pump comprising an integral casing having an unobstructed cylindrical chamber therein, a vane in said cylinder oscillating about ailxed axis concentric with the axis of said chamber, removable inlet and outlet abutments inserted within said cylindrical chamber and occupying the space therein outside the path of movement of said vane, outlet connections and valves located in the outlet abutment in communication with an outlet passage through said casing wall, and inlet connections formed in the cylinder walls behind the inlet abutment, said connections overlapping the ends of the vane when in their extreme position against the inlet abutment but not so overlapping when the vane is VICTOR GIDEON.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Description
March 20, 1934; .v GlDEON 1,951,607
REFRIGERATOR PUMP Filed April 9, 1932 3 Sheets-Sheet 2 w ic az fakieozz March 20, 1934. v D O 1,951,607
REFRIGERATOR PUMP Filed April 9, 1932 5 Sheets-Sheet 3 0507 fad 0 MINE Patented Ma 20,1934
PATENT osmcs momma PUMP v 111-, Ma orto Bom- Ohioa'lo, 111.. a mm- Application April a, 193:, Serial No. 604,185
reunion. zoo-15a) v This invention relates to oscillating pumps ior handling fluids such as refrigerants and has special reference to a balanced pump capable of high speed operation with mixtures of liquids and I gases without liability-from liquid hammer.
Ithas heretofore been necessary to sharply distinguish between liquid and gaseous pumps because ofthe detrimental efi'ect or compression clearances on the efllciency of the latter, a lack of such compression clearance resulting in liquid hammer if the pumps were operated at high speed while handling a refrigerant, for example, which carries entrained liquid. It is accordingly an important object of this invention to provide a pump capable of efficient high speed operation with mixtures of gases and liquids and one in which the pressures are balanced by either parallel or compound operation of a plurality of oscillating pumping elements. One advantage of the oscillatory type of pumping apparatus disclosed is that the piston elements have a harmonic motion similar to that of a pendulum wherein the dual stage of the compression stroke is provided by the decreasing velocity of the piston elements versal point is also subject to accurate initial con trcl which can be maintained in service to provide the minimum possible compression clearance.
It is a further object of this invention to provide a balanced oscillatory pump wherein each direction of movement produces one or more discharge strokes delivering either in parallel or in series, it being. desirable to compound the pump when working against high final pressures in or der to reduce the nicety of fitting required to work against high pressure difierences.
It is another object of this invention to pro vide a pump of the class described wherein the operation of the pump may be maintained at the initial high emciency by relieving the pumping parts of wear by eliminating therefrom any necessity of acting as bearing surfaces for maintaining self alignment and to take up play in the till driving connecting rod while maintaining the.
original center distance thereof.
It is also an object of this invention to provide an improved and simplified form or oscillatory pump that can be economically manufactured and that will maintain its original eiiiclency due o accurate alignment of the pumping elements which are subject only to fluid loads while in operation. It is still another object of this invention to provide an improved and simplified oscillatory pump or the class described which is self lubricatas they approach-the points of reversal, This re take up wear therein without changing the coning with the fluid being handled, which alsoserves to seal the pump shaft against leakage.
Other and further important objects of this invention will be apparent from the disclosures in the specification and the accompanying drawco ings.
This invention (in a preferred'iorm) is illustrated in the drawings and hereinafter more fully described.
On the drawings: v
Figure 1 is a side elevation of a pump embodying the features of this invention, together with its driving linkage.
Figure 2 is an enlarged vertical, longitudinal section thereof taken on the line II-II of Figure 1.
Figure 3 is an enlarged horizontal section on the line III-IE oi Figure 1.
Figure 4 showing the pump vane in a different position is a section on the line IV-IV of Figme 2.
Figure 5 is a section similar to Figure 4.
Figure 6 is a section showing a modified form of the invention arranged as a two stage pump.
Figure 7 is a section showing another modiflcaw tion involving foul-stages.
As shown on the drawings:
The general type of pump may conveniently be termed oscillatory as the pumping elements swing back and forth over an arcuate path as 35 distinguished from a completely rotary motion. Thus a shaft 10 is oscillated through a fixed angle hy means of a lever 11 and a connecting-rod 12 engaged on crankpins 13, one of which is bolted to a crank disc 14 which may be rotated by any w convenient prime mover, such for example as an electric motor. The. lever 11 is connected to the connecting rod by a second crankpln 13 shown in section in Figure 2, the bearing pin surface 15 thereof being i'rusto-oonical in form and engag- .ing in a complementary bearingsurface 16 in a bushing 17 which is clamped in an aperture in the rod 12 by a nut 18, a spring 19 being interposed between the nut and the end of bearing pin to maintain the some seated in the bushing to 1m necting rod center distance. Since the pump acts in both directions there will be no tendency towards unequal wear which might change the center distance.
A casing 20 provides a journal 21 for the shaft 10 and a cylindrical recess in one end of the cas ing, concentric with the shaft 10, forms the pump chamber 22, being closed by a cover 23 bolted thereto. The other end of the casing is provided 110 with an annular bolted-on flange 24 through which the shaft projects, a diaphragm type of seal 25 being clamped at its periphery between the flange 24 and the casing. The diaphragm provides for movement of an inner ring 26 of,
the seal longitudinally of the shaft, this ring being held against a collar 27 on the shaft by the fluid pressure generated in the pump, a spiral groove 28 being cut in the pump shaft to convey the fluid to the seal as well as distribute the fluid over the shaft to lubricate the same.
The shaft 10 carries a concentric hub 29 within the chamber 22, which hub is diametrically slotted to receive a vane 30 which is oscillated within the chamber 22 over a predetermined angle by the linkage previously described. Abutment members 31 and 32 are located between the hub 29 and the walls of the chamber 22 and are preferably keyed to the cover as shown at 33 in Figure 3. The member 31 in Figures 4 and 5 is on the suction side and is held in place by a cap screw 34 inserted through the suction or inlet connection 35. Suction or inlet passages 36 lead from the inlet connection to the compression side of the vane when the ends of the latter swing to the extreme right hand position shownat the top of Figure 5.
Similarly, the member 32 is located on the discharge side and is held by another cap screw 34 through the discharge or outlet connection 3'7. The discharge abutment contains discharge passages 38 leading therethrcugh to the outlet, these passages containing valve seats 39 for disc valves 40 backed by springs 41 and spring seats 42 threaded into the passages. The valve structure must be as light and quick acting as possible with the minimum compression space between the valve and the edge of the abutment against which the vane acts. It the two sides of the pump act in parallel, as in Figures 3, 4 and 5, the discharge passages 38 can be siamese as shown in these figures, while for series or compound action the passages must have separate inlets and outlets as shown in Figures 6 and 7.
The modification 01. Figure 6 involves a two stage pump differing from that previously described in that individual inlet connections 43 and 44 lead into the upper and lower pumping chambers, and individual outlets are provided at 45 and 46, the inlet 43 being the initial or suction inlet of the first stage, the corresponding outlet 45 being connected to the inlet 44 of the second stage, the outlet 46 of which is the pump delivery connection. In this form the inlets are preferably so positioned relative to the vane movements that one inlet is opened as the other closes. This arrangement obviates the need oi an intermediate reservoir between the first stage outlet and the second stage inlet, and both inlets are given the same relative timing to balance the worker the pump.
The modification of Figure '1 discloses a four stage pump wherein each side of each end of the vane delivers a charge during its movement away from the central position shown in the figure. In this form the discharge passages 38 are shown as positioned in the cylinder wall although it is to be understood that the previously described outlet abutment structure can be used if desired. Due to the sequence of compression strokes, if the connection 4'7 is chosen as the initial inlet, the corresponding outlet connection 48 delivers to the second stage inlet 49 on the same side but opposite end oi. the vane, and the second stage outlet 50 delivers to the third stage inlet 51 on the opposite side of the same end of the-vane. The third stage outlet 52 delivers to the fourth stage inlet 53, the fourth stage outlet 54 being the final pump delivery connection. It will be appreciated that if other conditions make the change-desirable, any of the inlets can be chosen for the, initial or suction inlet, in which case the sequence of connections is angularly shifted accordingly for a quadruple compound crank disc 14. The vane movement is intended to closely approach the surfaces of the inlet and outlet abutments at the extreme or reversal positions of the vane, the clearances being held to the minimum in the case of a pump intended to handle gasses. Since the shaft 10 holds the vane hub and vane concentric with the cylinder 22, the operating clearances may be set at the very minimum and will not be subject to wear in service as would be the case with reciprocating er rotary eccentric type of pumps. clearances can be set and will be maintained at the very minimum, so that entrained liquids will serve to seal the pump against loss of compression at normal operating speeds. Thus the pumping efilciency'will be maintained during service since the pumping elements are no more subject to wear than in a centrifugal type of pump although the pump is a positive displacement type suitable for handling gases or liquids or mixtures thereof.
It will thus be seen that I have invented an improved and simplified positive displacement oscillating pump that is especially suitable for handling mixtures of gases and liquids without eventual loss of efficiency due to wear therein.
I am aware that many changes may be made and numerous details of construction may be varied through a wide range without departing from the principles of this invention, and I, therefore, do not purpose limiting the patent granted hereon otherwise than necessitated by the prior art.
I claim as my invention:
An oscillatory pump comprising an integral casing having an unobstructed cylindrical chamber therein, a vane in said cylinder oscillating about ailxed axis concentric with the axis of said chamber, removable inlet and outlet abutments inserted within said cylindrical chamber and occupying the space therein outside the path of movement of said vane, outlet connections and valves located in the outlet abutment in communication with an outlet passage through said casing wall, and inlet connections formed in the cylinder walls behind the inlet abutment, said connections overlapping the ends of the vane when in their extreme position against the inlet abutment but not so overlapping when the vane is VICTOR GIDEON.
Thus the
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US604185A US1951607A (en) | 1932-04-09 | 1932-04-09 | Refrigerator pump |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US604185A US1951607A (en) | 1932-04-09 | 1932-04-09 | Refrigerator pump |
Publications (1)
Publication Number | Publication Date |
---|---|
US1951607A true US1951607A (en) | 1934-03-20 |
Family
ID=24418539
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US604185A Expired - Lifetime US1951607A (en) | 1932-04-09 | 1932-04-09 | Refrigerator pump |
Country Status (1)
Country | Link |
---|---|
US (1) | US1951607A (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4861236A (en) * | 1988-09-26 | 1989-08-29 | Ryon Kustes | Birotational pump |
WO2004088141A2 (en) * | 2003-04-02 | 2004-10-14 | Gebr. Becker Gmbh & Co. Kg | Oscillating piston pump |
US20180154869A1 (en) * | 2016-12-01 | 2018-06-07 | Fujitsu Ten Limited | Air compressor and extraneous-matter removing apparatus |
-
1932
- 1932-04-09 US US604185A patent/US1951607A/en not_active Expired - Lifetime
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4861236A (en) * | 1988-09-26 | 1989-08-29 | Ryon Kustes | Birotational pump |
US20070104600A1 (en) * | 2003-03-05 | 2007-05-10 | Sabine Meier | Oscillating piston pump |
WO2004088141A2 (en) * | 2003-04-02 | 2004-10-14 | Gebr. Becker Gmbh & Co. Kg | Oscillating piston pump |
WO2004088141A3 (en) * | 2003-04-02 | 2005-01-06 | Becker Gmbh & Co Kg Geb | Oscillating piston pump |
US20180154869A1 (en) * | 2016-12-01 | 2018-06-07 | Fujitsu Ten Limited | Air compressor and extraneous-matter removing apparatus |
US10717418B2 (en) * | 2016-12-01 | 2020-07-21 | Fujitsu Ten Limited | Air compressor and extraneous-matter removing apparatus |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US2043544A (en) | Rotary engine | |
US2604047A (en) | Two-stage hydraulic pressure pump | |
US2246272A (en) | Rotary pump | |
US1951607A (en) | Refrigerator pump | |
US2087772A (en) | Rotary engine | |
US2346014A (en) | Fluid pump | |
US1638183A (en) | Gyratory pump or compressor | |
US2343211A (en) | Reciprocating compressor | |
US2215873A (en) | Motor driven pump | |
US1749058A (en) | Rotary pump | |
US1468889A (en) | Multistage rotary pump | |
US3204563A (en) | Rotary piston engines | |
US2728297A (en) | Variable capacity pump | |
US2354980A (en) | Reciprocating pump | |
US2732126A (en) | Refrigerating apparatus | |
US2246273A (en) | Rotary pump | |
US2385730A (en) | Centrifugal pump | |
US1496704A (en) | Rotary pump for hydraulic transmission | |
US672970A (en) | Rotary motor or pump. | |
US2417816A (en) | Fluid pump or motor | |
US2246274A (en) | Rotary pump | |
US2290813A (en) | Compressor shaft seal | |
US1890560A (en) | Rotary pump and the like | |
US2653756A (en) | Plunger pump | |
US3259306A (en) | High pressure and high temperature refrigerant vapor compressor |