EP3354897A1 - Volumetric machine - Google Patents
Volumetric machine Download PDFInfo
- Publication number
- EP3354897A1 EP3354897A1 EP18151079.3A EP18151079A EP3354897A1 EP 3354897 A1 EP3354897 A1 EP 3354897A1 EP 18151079 A EP18151079 A EP 18151079A EP 3354897 A1 EP3354897 A1 EP 3354897A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compartment
- path
- channel
- compartments
- pressure
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 41
- 238000004891 communication Methods 0.000 claims abstract description 21
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 10
- 238000013459 approach Methods 0.000 claims description 4
- 238000000034 method Methods 0.000 claims description 4
- 238000011017 operating method Methods 0.000 claims description 2
- 230000002441 reversible effect Effects 0.000 claims description 2
- 230000003628 erosive effect Effects 0.000 description 6
- 229910000838 Al alloy Inorganic materials 0.000 description 1
- 229910001018 Cast iron Inorganic materials 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C2/00—Rotary-piston engines
- F03C2/08—Rotary-piston engines of intermeshing-engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
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- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
-
- 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
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
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- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
- F04C15/0023—Axial sealings for working fluid
- F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
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- 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
- F04C2240/00—Components
- F04C2240/30—Casings or housings
Definitions
- the present invention relates to a volumetric machine acting on an operating fluid, typically oil.
- This volumetric machine may be a pump or a motor or a machine that allows operation as a pump and as a motor alternatively.
- Volumetric gear pumps are known comprising two counter-rotating toothed wheels that engage with each other.
- the casing and the gears define a plurality of compartments for housing an operating fluid that necessarily move together with the toothed wheels that contribute to defining them.
- the pressure differential imposed on the pump is known.
- strong erosion is noted, particularly affecting the outlet end of the pressurisation outlet.
- the speed of the jet of oil exiting the pressurisation outlet increases as the pressure differential increases, which promotes the establishment of local cavitation phenomena.
- bubbles of gas dissolved in the oil (and possibly oil vapour) are formed, which then implode due to the fast pressurisation within the compartment (interposed between two teeth of the toothed wheel) which houses the outlet fluid. All this determines erosion which in a short time comprises the performance and operation of the pump.
- the technical task underlying the present invention is to propose a volumetric machine which obviates the drawbacks of the known art as described above.
- an object of the present invention is to provide a volumetric machine able to eliminate/minimise erosive phenomena.
- reference number 1 denotes a volumetric machine acting on an operating fluid.
- the volumetric machine 1 is a pump or a motor. It may be a machine that can operate alternatively as a motor or a pump.
- the volumetric machine 1 comprises a first toothed wheel 21.
- the first toothed wheel 21 comprises a first group 210 of teeth that identify interposed between them a first plurality 201 of compartments for the operating fluid.
- the first group 210 of teeth comprises all the teeth of the first wheel 21 ( figure 2 for illustrative simplicity 210 indicates only a part of the teeth of the first group). They extend along the circumference.
- the machine 1 comprises a second toothed wheel 22 comprising a second group 220 of teeth intended to engage with the teeth of the first group 210.
- the teeth of the second group 220 are all the teeth of the second wheel 22 (in figure 2 for illustrative simplicity 220 indicates only a part of the teeth of the second group).
- the axis of rotation of the first wheel 21 is parallel and distinct from that of the second wheel 22.
- the first and the second wheel 21, 22 are one outside the other (they partially co-penetrate at teeth that engage).
- the machine 1 comprises a casing 3 that defines a housing 30 for positioning the first toothed wheel 21.
- Such housing 30 also houses the second toothed wheel 22.
- the casing 3 is for example made of an aluminium alloy or cast iron.
- the machine 1 comprises a path 4 that extends along a portion of said casing 3.
- the path 4 may be a groove, for example a bevel.
- the path 4 places in fluid communication at least two compartments of said first plurality 201.
- the path 4 places in communication more than two compartments of the first plurality 201.
- the path 4 defines a sort of burr.
- the path 4 extends along an arc of a circumference.
- the path 4 in the case of a pump is called the pressurisation outlet.
- the path 4 in the case of a motor is known as the depressurisation outlet.
- the casing 3 comprises at least a first channel 51 distinct from said path 4. As exemplified in the figures the first channel 51 is separated from the path 4. They do not intersect.
- a compartment is defined upstream of another compartment if in the path that goes from an inlet mouth 28 of the fluid into the machine 1 to an outlet mouth 29 of the fluid from the machine 1 it is closer to the inlet mouth 28.
- the compartment 90a (hypothesizing that it is at the inlet mouth 28) will be upstream of the compartment 90b which is, in turn, upstream of the compartment 90c which is in turn upstream of the compartment 90d, which is in turn upstream of the compartment 90e which is in turn upstream of the compartment 90f which is in turn upstream of the compartment 90g.
- the inlet mouth 28 will be at the bottom and the outlet mouth 29 will be at the top (regardless of whether operation is as a motor or as a pump). Therefore, in the event of operating as a pump the environment at high and the environment at low pressure will be at the top and the bottom, respectively, whereas in the case of operation as a motor they will be inverted.
- the inlet mouth 28 and the outlet mouth 29 are respectively defined as the suction and delivery whereas in relation to a motor they are normally defined as the inlet and outlet.
- the second wheel 22 there will be a similar path to the path 4 and a similar passage to the first channel 51 (in figure 2 they have been indicated respectively by references 95 and 96). Also for the second wheel 22 what happens for the compartments of the first wheel 21 and their interaction with the path 95 and/or the passage 96 can be repeated.
- the predetermined configuration of the first wheel 21 may however not be simultaneous to a configuration of the second wheel 22 in which the passage 96 places in fluid communication two consecutive compartments (as illustrated in figure 2 ).
- the casing 3 comprises a first shim 300.
- the first shim 300 defines at least one cylindrical seat for housing a shaft of the first or of the second toothed wheel 21, 22.
- the first shim 300 comprises a surface that extends along a transversal plane (preferably orthogonal) to an axis of rotation of the first toothed wheel 21.
- the casing 3 comprises a second shim 9.
- the first wheel 21 is axially interposed between the first and the second shim 300, 9.
- the path 95 is appropriately afforded on the first shim 9.
- the casing 3 also comprises a lateral body 91 that axially surrounds the first wheel 21.
- the lateral body, the first and the second shim 91, 300, 9 define stator elements.
- the lateral body 91 is commonly defined as the pump body or motor body according to whether the machine 1 is a pump or a fluid dynamic motor.
- the first channel 51 is afforded on the first shim 300.
- the path 4 is advantageously afforded on the first shim 300.
- the additional passage 96 is advantageously afforded on the first shim 300. The description with reference to the first channel 51 may also be repeated for the additional passage 96.
- similar elements to the first channel 51 and/or to the path 4 and/or to the path 95 and/or to the passage 96 may also be present on the second shim 9.
- the first channel 51 can be afforded on the lateral body 91. Also in this case, there may be at least one additional channel (e.g. on the first shim 300).
- the volumetric machine 1 is a pump then the first channel 51 allows the first compartment 211 to be pressurised before it is overlapped with the outlet of the path 4. In this way, when such overlapping takes place the pressure in the first compartment 211 increases as an absolute value therefore the pressure difference to which the fluid is subjected at the outlet end of the path 4 is lower, thus reducing erosive phenomena.
- the first channel 51 allows the first compartment 211 to be partially depressurised before it is overlapped with the inlet of the path 4 (everything that is connected to the path 4 is connected to the low pressure environment). In this way, when the first compartment 211 is overlapped with the path 4 the pressure difference between the fluid present in the first compartment 211 and the fluid present in the path 4 is lower, therefore the erosion at the mouth of the path 4 is lower.
- the machine 1 allows a reversible operation, i.e. it allows correct operation in both rotation directions of the first wheel 21 (e.g. see figure 6 ).
- the casing 3 comprises a second channel 52 (see figure 6 ).
- the first channel 51 is useful during operation in a first rotation direction of the first wheel 21 (the clockwise one in figure 6 ) and the second channel 52 is useful during operation in a second rotation direction of the first wheel 21 opposite the first one (the anti-clockwise one in figure 6 ).
- the first channel 51 is part of a first pair 50 of channels arranged side by side, which in said predetermined configuration place in fluid communication the first and the second compartment 211, 212.
- the first channel 51 places in fluid communication the first and the second compartment 211, 212 for a rotation of the first toothed wheel 21 less than 10° (e.g. the first channel 51 could place in fluid communication the first and the second compartment 211, 212 for a rotation less than half the angular pitch of the first wheel 21).
- the time period in which the first channel 51 allows fluid communication between the first and the second compartment 211, 212 must be relatively contained.
- the passage section of the first channel 51 is relatively contained.
- the first channel 51 has a depth lower than 1.5 millimetres.
- the path 4 extends for an amplitude comprised between 60° and 70° and the depth of the first channel 51 is less than 0.5 millimetres.
- the path 4 extends for an amplitude comprised between 30° and 40° and the depth of the first channel is comprised between 0.7 and 1.5 millimetres.
- the first channel 51 is a pocket and has a preponderant extension direction 510 less than 20 millimetres.
- the fluid communication between the second compartment 212 and the path 4 starts in phase or in advance with respect to the fluid communication between the second compartment 212 and the first compartment 211.
- the second compartment 212 is placed in fluid communication with the path 4 in advance with respect to the fluid communication between the second compartment 212 and the first compartment 211 (such advance could be comprised between 2° and 8°). This is, for example, the case of the first solution described above.
- the second compartment 212 is placed in fluid communication with the first compartment 211 in phase with the path 4.
- the machine 1 may be a pump (or can however operate as a pump).
- the path 4 comprises a pressurisation groove of the second compartment 212. It increases the pressure of the second compartment 212 by placing it in communication with a compartment of the first plurality 201 placed downstream of said second compartment 212.
- the machine 1 may be a motor or may operate both as a motor and as a pump.
- the path 4 comprises a groove for depressurisation the second compartment 212.
- the path 4 therefore allows the pressure in the second compartment 212 to be reduced by placing it in contact with a compartment placed downstream (which is at a lower pressure i.e. at the pressure available at the outlet mouth 29 of the volumetric machine 1).
- the method comprises the step of making the first and the second toothed wheel 21, 22 rotate. In this way the fluid flows into the first plurality 201 of compartments and is moved between the inlet mouth 28 and the outlet mouth 29.
- the first and second wheel 21, 22 are counter-rotating.
- the method comprises the steps of:
- the ordinates show the ratio between the pressure in the first compartment 211 and the pressure at the outlet mouth 29 as a function of the rotation angle of the first wheel 21.
- This graph in the case of a pump, is to be read from left to right. In the case of operation as a motor it should be read from right to left.
- Curve A shows the pressure increase in the event of a machine 1 operating as a pump in compliance with the present invention.
- the other curves instead relate to a machine outside the scope of the present invention.
- curves B and C show the pressure profile in the case in which the path 4 is absent.
- Curve D shows the pressure profile in the case in which the path 4 is present, but the first channel 51 is absent and it is therefore not possible to establish a priori when the compartment is pressurised.
- the invention achieves important advantages.
- first channel 51 that allows the pressure passage from the inlet mouth 28 to the outlet mouth 29 to be split into two steps. It can therefore be defined as a pre-pressurisation pocket (in the case of a pump) or a pre-depressurisation pocket (in the case of a motor).
- the invention as it is conceived is susceptible to numerous modifications and variants, all falling within the scope of the inventive concept characterising it. Further, all the details can be replaced with other technically-equivalent elements. In practice, all the materials used, as well as the dimensions, can be any according to requirements.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Rotary Pumps (AREA)
- Formation And Processing Of Food Products (AREA)
Abstract
i) a first toothed wheel (21) comprising a first group (210) of teeth that identify interposed between them a first plurality (201) of compartments for the operating fluid;
ii) a second toothed wheel (22) comprising a second group (220) of teeth intended to engage with the teeth of the first group (210);
iii) a casing (3) that defines a housing (30) for positioning the first and the second toothed wheel (21, 22);
iv) a path (4) that extends along a section of said casing (3) and that places in fluid communication at least two compartments of said first plurality (201).
- the first channel (51) places in fluid communication a first and a second compartment (211, 212) of said first plurality (201) which are consecutive and at least partially delimited by a same tooth of the first group (210);
- at least the first compartment (211) of the first plurality (201) being distinct from compartments of the first plurality (201) licked by said path (4);
- said second compartment (212) being licked by the path (4);
- said first compartment (211) being placed upstream of the second compartment (212) and of the compartments of the first plurality (201) licked by said path (4).
Description
- The present invention relates to a volumetric machine acting on an operating fluid, typically oil. This volumetric machine may be a pump or a motor or a machine that allows operation as a pump and as a motor alternatively.
- Volumetric gear pumps are known comprising two counter-rotating toothed wheels that engage with each other.
- They are housed in a closed pump body on two opposite faces by two distinct shims that extend orthogonally to the axis of rotation of the two toothed wheels.
- The casing and the gears define a plurality of compartments for housing an operating fluid that necessarily move together with the toothed wheels that contribute to defining them.
- The need to have high volumetric and hydro-mechanical performance requires knowing how to accurately control the law of pressurisation the oil compartment during the rotation of the toothed wheels. For this purpose, circumferential processes are used to form pressurisation outlets on the surfaces of the shims.
- They allow oil to be conveyed from the high pressure environment to a compartment in a position defined by the designer. Thus it is certain that as the rotation speed of the pump changes, the axial balance of forces acting on the shims remains constant, preventing the occurrence of seizure (in the event that the shim is excessively pushed towards the toothed wheels) or in low volumetric performance conditions (in the event that the toothed wheels move away from the shim).
- Hence, once the pressure values at the suction and at the delivery have been fixed, the pressure differential imposed on the pump is known. As the pressure differential increases, strong erosion is noted, particularly affecting the outlet end of the pressurisation outlet. This is connected with the fact that the speed of the jet of oil exiting the pressurisation outlet increases as the pressure differential increases, which promotes the establishment of local cavitation phenomena. In practice, bubbles of gas dissolved in the oil (and possibly oil vapour) are formed, which then implode due to the fast pressurisation within the compartment (interposed between two teeth of the toothed wheel) which houses the outlet fluid. All this determines erosion which in a short time comprises the performance and operation of the pump.
- In this context, the technical task underlying the present invention is to propose a volumetric machine which obviates the drawbacks of the known art as described above.
- In particular, an object of the present invention is to provide a volumetric machine able to eliminate/minimise erosive phenomena.
- The stated technical task and specified objects are substantially achieved by a volumetric machine comprising the technical features disclosed in one or more of the appended claims.
- Further characteristics and advantages of the present invention will become more apparent from the approximate and thus non-limiting description of a preferred, but not exclusive, embodiment of a volumetric machine, as illustrated in the accompanying drawings, in which:
-
figure 1 shows a simplified exploded view of a volumetric machine according to the present invention; -
figure 2 shows a view of a volumetric machine according to the present invention; -
figure 3 shows an enlargement of a detail offigure 2 ; -
figure 4 shows a sectional view of a detail of a volumetric machine according to the present invention; -
figure 5 shows a comparative graph; -
figure 6 shows a volumetric machine according to the present invention and alternative to that offigure 2 ; -
figure 7 shows a volumetric machine according to the present invention, alternative to that offigure 2 or6 ; -
figure 8 shows portions of a volumetric machine according to the present invention alternative to that offigure 2 or6 or7 ; - In the appended figures,
reference number 1 denotes a volumetric machine acting on an operating fluid. - Typically the operating fluid is oil. The
volumetric machine 1 is a pump or a motor. It may be a machine that can operate alternatively as a motor or a pump. - The
volumetric machine 1 comprises a firsttoothed wheel 21. - The first
toothed wheel 21 comprises afirst group 210 of teeth that identify interposed between them afirst plurality 201 of compartments for the operating fluid. Appropriately thefirst group 210 of teeth comprises all the teeth of the first wheel 21 (figure 2 forillustrative simplicity 210 indicates only a part of the teeth of the first group). They extend along the circumference. - The
machine 1 comprises a secondtoothed wheel 22 comprising asecond group 220 of teeth intended to engage with the teeth of thefirst group 210. The teeth of thesecond group 220 are all the teeth of the second wheel 22 (infigure 2 forillustrative simplicity 220 indicates only a part of the teeth of the second group). Throughout the present description everything described with reference to thefirst wheel 21 can also be repeated for thesecond wheel 22. The axis of rotation of thefirst wheel 21 is parallel and distinct from that of thesecond wheel 22. The first and thesecond wheel - Appropriately the
machine 1 comprises acasing 3 that defines ahousing 30 for positioning the firsttoothed wheel 21.Such housing 30 also houses the secondtoothed wheel 22. Thecasing 3 is for example made of an aluminium alloy or cast iron. - The
machine 1 comprises apath 4 that extends along a portion of saidcasing 3. Thepath 4 may be a groove, for example a bevel. Thepath 4 places in fluid communication at least two compartments of saidfirst plurality 201. In particular, thepath 4 places in communication more than two compartments of thefirst plurality 201. Appropriately, thepath 4 defines a sort of burr. Preferably, thepath 4 extends along an arc of a circumference. Thepath 4 in the case of a pump is called the pressurisation outlet. Thepath 4 in the case of a motor is known as the depressurisation outlet. - The
casing 3 comprises at least afirst channel 51 distinct from saidpath 4. As exemplified in the figures thefirst channel 51 is separated from thepath 4. They do not intersect. - At least in one predetermined configuration assumed by the first wheel 21:
- the
first channel 51 places in fluid communication a first and asecond compartment first plurality 201 which are consecutive and at least partially delimited by a same tooth of the first group 210 (thefirst channel 51 allows a by-pass of the tooth in said predetermined configuration); - at least the
first compartment 211 of thefirst plurality 201 is distinct from (all the) compartments of thefirst plurality 201 licked by said path 4 (i.e. the compartments that face thepath 4; for example with reference tofigure 7 they are thecompartments first compartment 211 is not licked directly by thepath 4; - the
second compartment 212 is, instead, licked by thepath 4; - the
first compartment 211 is placed upstream of thesecond compartment 212 and of the compartments of thefirst plurality 201 licked by thepath 4. Such predetermined configuration photographs the situation at a particular angle of rotation of the first toothed wheel 21 (for examplefigure 2 ,3 ,4 ,6 ,7 ). - Throughout the present description a compartment is defined upstream of another compartment if in the path that goes from an
inlet mouth 28 of the fluid into themachine 1 to anoutlet mouth 29 of the fluid from themachine 1 it is closer to theinlet mouth 28. For example, infigure 7 thecompartment 90a (hypothesizing that it is at the inlet mouth 28) will be upstream of thecompartment 90b which is, in turn, upstream of thecompartment 90c which is in turn upstream of thecompartment 90d, which is in turn upstream of thecompartment 90e which is in turn upstream of thecompartment 90f which is in turn upstream of thecompartment 90g. For example, in the case offigure 2 , once the clockwise rotation direction of the firsttoothed wheel 21 has been set, theinlet mouth 28 will be at the bottom and theoutlet mouth 29 will be at the top (regardless of whether operation is as a motor or as a pump). Therefore, in the event of operating as a pump the environment at high and the environment at low pressure will be at the top and the bottom, respectively, whereas in the case of operation as a motor they will be inverted. - In technical jargon, in relation to a pump, the
inlet mouth 28 and theoutlet mouth 29 are respectively defined as the suction and delivery whereas in relation to a motor they are normally defined as the inlet and outlet. - Also for the
second wheel 22 there will be a similar path to thepath 4 and a similar passage to the first channel 51 (infigure 2 they have been indicated respectively byreferences 95 and 96). Also for thesecond wheel 22 what happens for the compartments of thefirst wheel 21 and their interaction with thepath 95 and/or thepassage 96 can be repeated. The predetermined configuration of thefirst wheel 21 may however not be simultaneous to a configuration of thesecond wheel 22 in which thepassage 96 places in fluid communication two consecutive compartments (as illustrated infigure 2 ). - The
casing 3 comprises afirst shim 300. Thefirst shim 300 defines at least one cylindrical seat for housing a shaft of the first or of the secondtoothed wheel - Appropriately the
first shim 300 comprises a surface that extends along a transversal plane (preferably orthogonal) to an axis of rotation of the firsttoothed wheel 21. Likewise, thecasing 3 comprises asecond shim 9. Thefirst wheel 21 is axially interposed between the first and thesecond shim path 95 is appropriately afforded on thefirst shim 9. - The
casing 3 also comprises alateral body 91 that axially surrounds thefirst wheel 21. The lateral body, the first and thesecond shim lateral body 91 is commonly defined as the pump body or motor body according to whether themachine 1 is a pump or a fluid dynamic motor. - As exemplified in
figures 2 ,3 ,4 ,6 and7 thefirst channel 51 is afforded on thefirst shim 300. Also thepath 4 is advantageously afforded on thefirst shim 300. Possibly theadditional passage 96 is advantageously afforded on thefirst shim 300. The description with reference to thefirst channel 51 may also be repeated for theadditional passage 96. - Advantageously, similar elements to the
first channel 51 and/or to thepath 4 and/or to thepath 95 and/or to thepassage 96 may also be present on thesecond shim 9. - As exemplified in
figure 8 , thefirst channel 51 can be afforded on thelateral body 91. Also in this case, there may be at least one additional channel (e.g. on the first shim 300). - If the
volumetric machine 1 is a pump then thefirst channel 51 allows thefirst compartment 211 to be pressurised before it is overlapped with the outlet of thepath 4. In this way, when such overlapping takes place the pressure in thefirst compartment 211 increases as an absolute value therefore the pressure difference to which the fluid is subjected at the outlet end of thepath 4 is lower, thus reducing erosive phenomena. - Alternatively, if the
volumetric machine 1 is a motor the first channel 51 (seefigure 2 ) allows thefirst compartment 211 to be partially depressurised before it is overlapped with the inlet of the path 4 (everything that is connected to thepath 4 is connected to the low pressure environment). In this way, when thefirst compartment 211 is overlapped with thepath 4 the pressure difference between the fluid present in thefirst compartment 211 and the fluid present in thepath 4 is lower, therefore the erosion at the mouth of thepath 4 is lower. - In a particular embodiment the
machine 1 allows a reversible operation, i.e. it allows correct operation in both rotation directions of the first wheel 21 (e.g. seefigure 6 ). - For this purpose the
casing 3 comprises a second channel 52 (seefigure 6 ). In that case thefirst channel 51 is useful during operation in a first rotation direction of the first wheel 21 (the clockwise one infigure 6 ) and thesecond channel 52 is useful during operation in a second rotation direction of thefirst wheel 21 opposite the first one (the anti-clockwise one infigure 6 ). - In a pre-established configuration that may coincide or not with the predetermined configuration mentioned above:
- the
second channel 52 places in fluid dynamic connection a third andfourth compartment first plurality 201 of compartments; - the
fourth compartment 214 is distinct from the compartments of thefirst plurality 201 licked by the path 4 (thethird compartment 213 is instead licked by the path 4); - the
path 4 is interposed between the first and thesecond channel figure 6 ), thepath 4 is interposed between the first and thefourth compartment - In the solution exemplified in
figure 7 thefirst channel 51 is part of afirst pair 50 of channels arranged side by side, which in said predetermined configuration place in fluid communication the first and thesecond compartment - The
first channel 51 places in fluid communication the first and thesecond compartment toothed wheel 21 less than 10° (e.g. thefirst channel 51 could place in fluid communication the first and thesecond compartment first channel 51 allows fluid communication between the first and thesecond compartment - For similar reasons, the passage section of the
first channel 51 is relatively contained. - Typically, the
first channel 51 has a depth lower than 1.5 millimetres. For example, in a first embodiment thepath 4 extends for an amplitude comprised between 60° and 70° and the depth of thefirst channel 51 is less than 0.5 millimetres. In a second example embodiment thepath 4 extends for an amplitude comprised between 30° and 40° and the depth of the first channel is comprised between 0.7 and 1.5 millimetres. Appropriately thefirst channel 51 is a pocket and has apreponderant extension direction 510 less than 20 millimetres. - To reach said predetermined configuration, the fluid communication between the
second compartment 212 and thepath 4 starts in phase or in advance with respect to the fluid communication between thesecond compartment 212 and thefirst compartment 211. - For example, to reach said predetermined configuration, the
second compartment 212 is placed in fluid communication with thepath 4 in advance with respect to the fluid communication between thesecond compartment 212 and the first compartment 211 (such advance could be comprised between 2° and 8°). This is, for example, the case of the first solution described above. - Alternatively, the
second compartment 212 is placed in fluid communication with thefirst compartment 211 in phase with thepath 4. As indicated above, themachine 1 may be a pump (or can however operate as a pump). In that case, thepath 4 comprises a pressurisation groove of thesecond compartment 212. It increases the pressure of thesecond compartment 212 by placing it in communication with a compartment of thefirst plurality 201 placed downstream of saidsecond compartment 212. - The
machine 1 may be a motor or may operate both as a motor and as a pump. With reference tofigure 2 , in the case of operation as a motor, thepath 4 comprises a groove for depressurisation thesecond compartment 212. Thepath 4 therefore allows the pressure in thesecond compartment 212 to be reduced by placing it in contact with a compartment placed downstream (which is at a lower pressure i.e. at the pressure available at theoutlet mouth 29 of the volumetric machine 1). - Further subject matter of the present invention is an operating method of a volumetric machine having one or more of the characteristics described hereinabove.
- The method comprises the step of making the first and the second
toothed wheel first plurality 201 of compartments and is moved between theinlet mouth 28 and theoutlet mouth 29. - Likewise the fluid is moved by the second
toothed wheel 22. This happens in the same way as in thefirst wheel 21. - The first and
second wheel - In the predetermined configuration described above, the method comprises the steps of:
- making the pressure of the
second compartment 212 approach that of or be uniform with one of the compartments of thefirst plurality 201 placed downstream of thesecond compartment 212 through said path 4 (such step could however take place or at least begin before reaching said predetermined configuration); - making the pressure of the
first compartment 211 approach that of thesecond compartment 212 through saidfirst channel 51, in such a way that the pressure in thefirst compartment 211 becomes intermediate between the pressure in thesecond compartment 212 and the pressure of theinlet mouth 28. Appropriately (at the end of the step of making the pressure of thefirst compartment 211 approach that of thesecond compartment 212 through said first channel 51) the absolute pressure difference value between a point of thefirst compartment 211 and a point of theinlet mouth 28 of themachine 1 may be comprised between 30% and 70% of the absolute pressure variation value between theinlet mouth 28 and theoutlet mouth 29 of the fluid. - In
figure 5 the ordinates show the ratio between the pressure in thefirst compartment 211 and the pressure at theoutlet mouth 29 as a function of the rotation angle of thefirst wheel 21. This graph, in the case of a pump, is to be read from left to right. In the case of operation as a motor it should be read from right to left. - Curve A shows the pressure increase in the event of a
machine 1 operating as a pump in compliance with the present invention. The other curves instead relate to a machine outside the scope of the present invention. In fact, curves B and C show the pressure profile in the case in which thepath 4 is absent. Curve D shows the pressure profile in the case in which thepath 4 is present, but thefirst channel 51 is absent and it is therefore not possible to establish a priori when the compartment is pressurised. - The invention achieves important advantages.
- In particular it allows the erosive phenomena that occur at one of the two ends of the
path 4 to be eliminated or however reduced. With reference tofigure 2 this is obtained through afirst channel 51 that allows the pressure passage from theinlet mouth 28 to theoutlet mouth 29 to be split into two steps. It can therefore be defined as a pre-pressurisation pocket (in the case of a pump) or a pre-depressurisation pocket (in the case of a motor). The invention as it is conceived is susceptible to numerous modifications and variants, all falling within the scope of the inventive concept characterising it. Further, all the details can be replaced with other technically-equivalent elements. In practice, all the materials used, as well as the dimensions, can be any according to requirements.
Claims (10)
- A volumetric machine acting on an operating fluid, comprising:- a first toothed wheel (21) comprising a first group (210) of teeth that identify interposed between them a first plurality (201) of compartments for the operating fluid;- a second toothed wheel (22) comprising a second group (220) of teeth intended to engage with the teeth of the first group (210);- a casing (3) that defines a housing (30) for positioning the first and the second toothed wheel (21, 22);- a path (4) that extends along a section of said casing (3) and that places in fluid communication at least two compartments of said first plurality (201);said volumetric machine being a pump and/or fluid dynamic motor; characterised in that the casing (3) comprises at least one first channel (51) distinct from said path (4); at least in a predetermined configuration assumed by the first wheel (21):- the first channel (51) places in fluid communication a first and a second compartment (211, 212) of said first plurality (201) which are consecutive and at least partially delimited by a same tooth of the first group (210);- at least the first compartment (211) of the first plurality (201) being distinct from the compartments of the first plurality (201) licked by said path (4);- said second compartment (212) being licked by the path (4);- said first compartment (211) being placed upstream of the second compartment (212) and of the compartments of the first plurality (201) licked by said path (4).
- The machine according to claim 1, characterised in that the casing (3) comprises a first shim (300) on which said first channel (51) is afforded.
- The machine according to claim 1 or 2, characterised in that said first channel (51) has a depth of less than 1.5 millimetres.
- The machine according to any one of the preceding claims, characterised in that the path (4) extends along an arc of circumference.
- The machine according to any one of the preceding claims, characterised in that it allows a reversible operation in both directions of rotation of the first toothed wheel (21), said casing (3) comprising a second channel (52);
in a pre-established configuration that may coincide or not with said predetermined configuration:- the second channel (52) places in fluid dynamic connection a third and fourth compartment (213, 214) of said first plurality (201) of compartments;- the fourth compartment (214) is distinct from the compartments of the first plurality (201) licked by the path (4);- the path (4) is interposed between the first and the second channel (51, 52). - The machine according to any one of the preceding claims, characterised in that the first channel (51) is part of a first pair (50) of channels arranged side by side, which in the predetermined configuration place in fluid communication the first and the second compartment (211, 212).
- The machine according to any one of the preceding claims, characterised in that the first channel (51) places in fluid communication the first and the second compartment (211, 212) for a rotation of the first toothed wheel (21) less than 10°.
- The machine according to any one of the preceding claims, characterised in that it is:- a pump, said path (4) comprising a pressurisation groove of the second compartment (212) which increases the pressure of the second compartment (212) placing it in communication with a compartment of the first plurality (201) placed downstream of said second compartment (212); or- a motor, said path (4) comprising a depressurisation groove of the second compartment (212) which permits the pressure of the second compartment (212) to be reduced by putting it in contact with a compartment of the first plurality which is placed downstream and is located at a lower pressure.
- The machine according to any one of the preceding claims, characterised in that the first channel (51) is a pocket and has a predominant extension direction (510) of less than 20 millimetres.
- An operating method of a volumetric machine according to any one of claims 1 to 9, comprising the step of making the first and the second toothed wheel (21, 22) turn, making the fluid flow into the first plurality (201) of compartments and moving it between an inlet mouth (28) in the machine (1) and an outlet mouth (39) from the machine (1);
in said predetermined configuration, the method comprises the step of making the pressure of the first compartment (211) approach that of the second compartment (212) through said first channel (51), in such a way that the pressure in the first compartment (211) becomes intermediate between the pressure in the second compartment (212) and the pressure of the inlet mouth (28).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT102017000010437A IT201700010437A1 (en) | 2017-01-31 | 2017-01-31 | VOLUMETRIC MACHINE |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3354897A1 true EP3354897A1 (en) | 2018-08-01 |
EP3354897B1 EP3354897B1 (en) | 2023-11-29 |
Family
ID=58995120
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18151079.3A Active EP3354897B1 (en) | 2017-01-31 | 2018-01-10 | Volumetric machine |
Country Status (3)
Country | Link |
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EP (1) | EP3354897B1 (en) |
CN (1) | CN108374749B (en) |
IT (1) | IT201700010437A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10858940B1 (en) | 2019-06-17 | 2020-12-08 | Hamilton Sundstrand Corporation | Bearing with an asymmetric pressure balance groove |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3263620A (en) * | 1964-02-07 | 1966-08-02 | Chandler Evans Inc | Light weight bearings for gear pumps |
GB1224566A (en) * | 1967-12-27 | 1971-03-10 | Koehring Co | Pressure loaded gear pump |
WO2014168830A2 (en) * | 2013-04-11 | 2014-10-16 | Caterpillar Inc. | Gear pump having grooved mounting adapter |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2695566A (en) * | 1950-05-19 | 1954-11-30 | Borg Warner | Pump, bushing graduated pressure responsive areas |
CN85107186B (en) * | 1985-09-29 | 1988-11-16 | 程安强 | Asymmetry type radial floating gear pump and its motor |
CN2883735Y (en) * | 2006-04-18 | 2007-03-28 | 四川省机械研究设计院 | Embedded high temp geared pump |
DE102006025182A1 (en) * | 2006-05-30 | 2007-12-06 | Trw Automotive Gmbh | Gear pump, in particular for a power steering |
CN204591667U (en) * | 2015-03-02 | 2015-08-26 | 嵊州市东歌机械设备有限公司 | A kind of chemical industry cam pump of corrosion-and high-temp-resistant |
-
2017
- 2017-01-31 IT IT102017000010437A patent/IT201700010437A1/en unknown
-
2018
- 2018-01-10 EP EP18151079.3A patent/EP3354897B1/en active Active
- 2018-01-22 CN CN201810059788.1A patent/CN108374749B/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3263620A (en) * | 1964-02-07 | 1966-08-02 | Chandler Evans Inc | Light weight bearings for gear pumps |
GB1224566A (en) * | 1967-12-27 | 1971-03-10 | Koehring Co | Pressure loaded gear pump |
WO2014168830A2 (en) * | 2013-04-11 | 2014-10-16 | Caterpillar Inc. | Gear pump having grooved mounting adapter |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10858940B1 (en) | 2019-06-17 | 2020-12-08 | Hamilton Sundstrand Corporation | Bearing with an asymmetric pressure balance groove |
EP3754158A1 (en) * | 2019-06-17 | 2020-12-23 | Hamilton Sundstrand Corporation | Bearing with an asymmetric pressure balance groove |
Also Published As
Publication number | Publication date |
---|---|
CN108374749A (en) | 2018-08-07 |
EP3354897B1 (en) | 2023-11-29 |
IT201700010437A1 (en) | 2018-07-31 |
CN108374749B (en) | 2021-08-17 |
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