EP3102826A1 - Compressor for a compressed air system in particular for a motor vehicle - Google Patents
Compressor for a compressed air system in particular for a motor vehicleInfo
- Publication number
- EP3102826A1 EP3102826A1 EP15702759.0A EP15702759A EP3102826A1 EP 3102826 A1 EP3102826 A1 EP 3102826A1 EP 15702759 A EP15702759 A EP 15702759A EP 3102826 A1 EP3102826 A1 EP 3102826A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- chamber
- compressor
- suction
- pressure chamber
- 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.)
- Withdrawn
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B25/00—Multi-stage pumps
- F04B25/005—Multi-stage pumps with two cylinders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
- F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
Definitions
- Compressor for a compressed air system in particular of a motor vehicle
- the invention relates to a compressor according to the features of the preamble of claim 1.
- compressors are used to provide the necessary for the operation of the brake system and ancillaries compressed air. These compressors are usually coupled directly to the combustion engine.
- Compressors or compressors of the above type can be designed differently.
- piston compressor which consist in principle of a housing with crankshaft, connecting rods, pistons and suction and pressure valves.
- gas in particular air
- the intake valve closes and the air is compressed in the cylinder.
- the air is compressed to a part of its original volume while increasing the pressure in the cylinder.
- the increased pressure in the cylinder acts on a spring-loaded pressure valve.
- a two-stage compressor basically consists of two compressors connected in series. In the first, the air from the ambient pressure through a first Saugkamnner sucked and compressed to a higher pressure in a first pressure chamber. After intermediate cooling, the air in the second compressor stage is further compressed. In the case of two or more stages of compaction, the mechanical stress on the components subjected to pressure is reduced, thereby achieving a longer service life of the compressors.
- an intermediate cooling is provided as a rule.
- the cooling in the intercooler allows the compression to a final pressure with reduced power consumption and lower pressure gas temperature.
- EP 1650434 A1 discloses a multistage piston compressor with reduced power consumption in the absence of backpressure (idling).
- the multistage reciprocating compressor for compressing compressible media comprises at least one upstream and at least one downstream compressor stage, each compressor stage comprising at least one piston guided in a cylinder chamber and one inlet valve chamber connected to the cylinder chamber through an inlet valve and one outlet valve chamber connected to the cylinder chamber through an outlet valve , and is characterized in that at least one upstream compressor stage, the inlet valve chamber is connected by at least one additional valve to the cylinder chamber, which is in an open position at rest and moves to a closed position when the differential pressure in the Auslassventilhunt furthest downstream compressor stage exceeds a predetermined value.
- This relief system is controlled by the pressure difference between the pressure chamber and the cylinder chamber of the first stage and provides when falling below a certain pressure in the pressure chamber, a connection between the Cylinder space of the first stage and the suction chamber ago, which is arranged before the first stage.
- the first stage is ineffective and only the second stage of the compressor continues to promote air from the suction in the downstream pressure line.
- the so-called automatic relief system is very robust, since no external controls are necessary.
- the disadvantage is - especially in vehicle use - the delayed achievement of the full capacity (the start of the compressor idling) at a largely empty pressure vessel. This leads (in relation to the actual delivery volume of the compressor initially only to a low flow rate for filling) to an extended filling time of the pressure vessel.
- the object of the invention is to provide a device by means of which the increase in the flow rate of the previously described compressors in the lower pressure range is possible, without sacrificing the benefits of multi-stage, such as higher efficiency or lower compression end temperatures.
- a development should provide that a reduced response time is given to the signal "idle” or “promote” what is needed especially for commercial vehicles.
- the basic idea of the invention is that the switching and release system uses as a signal the pressure of the pressure chamber and / or a control signal of an external control, for example a pressure signal of a control line.
- a switching of the compressor acts such that the second stage sucks directly from the suction chamber and promotes the first stage directly into the pressure chamber.
- a two-stage air compressor is formed into a single-stage air compressor with two working chambers / cylinders (with intake volume increased by the second stage intake volume), in which the total intake volume in comparison to the two-stage mode by the intake volume of second cylinder is increased.
- the function is also applicable to more than two-stage compressors.
- the main advantage of the invention consists in the fact that the flow rate of the compressor is increased in the lower pressure range, without adversely affecting the provided by the multi-stage principle higher efficiency or the lower compression end temperatures.
- the filling times or response times are thereby considerably shorter and lead to a sufficient amount of air, especially in the lower pressure range.
- the advantage is given that falls below a previously defined pressure, which is measured in the first pressure chamber, the second stage sucks the air directly from the suction chamber.
- the first piston compresses directly into this pressure chamber.
- This causes a single-stage compressor is present, however, has a significantly higher intake volume and thus also provides the appropriate amount of air. If the limit value of the pressure in the pressure chamber is exceeded again, the original state is restored. Switching can be done by simple valve technology.
- the compressor according to the invention allows three modes of operation:
- the concept essential to the invention is to convert an air compressor in an existing cylinder head from a two-stage to a single-stage (and vice versa).
- the reversal is advantageously carried out in the cylinder head of the air compressor, with the additional option to combine simultaneously with a relief system.
- the unloading system can be controlled automatically or externally.
- the invention is not limited to a two-stage compressor. Rather, a multi-stage operation of compressors may be provided, which can be converted into the single-stage operation by interconnecting to a common suction chamber and a common pressure chamber. Furthermore, any combinations by interconnection are conceivable. For example, a compressor consisting of three cylinders can be converted into a two-stage operation.
- the invention advantageously finds application for air compressors, in particular for motor vehicles. It is not limited to this. Therefore, only compressors are referred to below, any type of compressor, including air or gas compressor, understood.
- FIG. 1 shows a longitudinal section through the compressor in the plane of FIG
- Cylinder axes with the unloading system inactive a horizontal section through the cylinder head of the compressor in the height of the upper overflow along a line III-III of Figure 1 in the two-stage conveying mode. a horizontal section through the cylinder head in the height of the lower overflow along a line IV-IV of Figure 1 in two-stage operation. a section through the compressor of Figure 1 along a line II-II (control plane) of FIG. 1; a vertical section through the control valves with open first transfer port and closed second and third transfer port; a horizontal section through the cylinder head in height of the upper transfer ports along the line III-III of Figure 1 in single-stage operation. a horizontal section through the cylinder head along a line IV-IV of Figure 1, in single-stage operation.
- FIGS. 1 and 2 show a schematic illustration of an automatic or externally controllable unloading system of a compressor 1.
- the relief system 1 is designed for a compressor system which is based on a two-stage process or on two stages Z1 and Z2, Z1 standing for the first stage and Z2 for the second stage.
- the cylinder head of the compressor 1 is divided into two overflow channel planes 2, 3 and into a control plane 4.
- the cylinder head has two relief valves 5, 6 and two control valves 7, 8 (designed as directional control valves).
- the compressor 1 further comprises two pistons 9a, 10a, each movable in a cylinder chamber 9, 10, wherein the first cylinder chamber 9 comprises a first suction chamber 11 and a first pressure chamber 12 and the second cylinder chamber 10 comprises a second suction chamber 13 and a second pressure chamber 14.
- the compressor 1 shows a longitudinal section through the compressor 1 in the plane of the axes of the cylinder. Shown are the relief valves 5, 6 in the closed state.
- the compressor 1 is designed so that all modes of operation, namely "two-stage conveying” or “single-stage conveying” or “idling" are executable.
- 2 shows a horizontal section through the cylinder head at the level of the upper transfer port plane 2 and represents a two-stage process.
- the first transfer port 15 connects the first pressure chamber 12 with the second suction chamber 13 (flow direction indicated by arrows in FIG. 2).
- the first pressure chamber 12 of the first stage Z1 represents an intermediate chamber which is also the second stage suction chamber Z2 (due to the fluid communication caused by the illustrated position of the control valve 7) without the regular division into two sub-chambers (with to leave the corresponding stages Z1 and Z2).
- the overflow channel 15 is released from the piston of the control valve 7. This is pressurized with appropriate pressure.
- FIG. 3 shows a horizontal section through the cylinder head at the level of the further overflow channel plane 3.
- the further overflow channel 16 connects the first suction chamber 11 to the further suction chamber 13.
- the third overflow channel 17 connects the first pressure chamber 12 to the second pressure chamber 14 , is also closed. These are closed in two-stage operation by the pistons of the control valves 7, 8, so that the process of FIG. 2 is executable.
- FIG. 4 shows a section through the control plane 4 of the compressor 1 according to FIG. 1.
- This control plane 4 comprises control channels 18, 19, which act on the control chambers of the two control valves 7, 8 and the two relief valves 5, 6 with the pressure p3 of the second pressure chamber 14. If a lower limit of the said pressure, which has been previously defined and set, is undershot, switching from the two-stage to the single-stage operation takes place. If an upper limit is exceeded, it is switched to the idle mode.
- Fig. 5 shows a vertical section through the cylinder head of the compressor 1 in two-stage operation.
- the control valves 7, 8 are acted upon by the pressure p3 and thus release the first overflow channel 15.
- the further transfer channels 16, 17 are closed.
- a compressor 1 is provided in order to increase in particular the flow rate with a small back pressure (in the lower speed range).
- This compressor 1 causes preferably a self-switching takes place from the two-stage in the single-stage operating mode.
- FIG. 6 shows the operating mode "single-stage operation."
- the piston of the first control valve 7 is positioned such that the first overflow channel 15 is closed
- the section through the further overflow channel plane 3, shown in Fig. 7 and 8, shows that the two suction chambers 1 1, 13 via the further overflow channel 16 and the two pressure chambers 12, 14 via the third overflow channel 17 with each other by the corresponding position
- the two-stage compressor 1 shown here is changed over to a single-stage compressor 1 with a total intake volume increased by the intake volume of the second stage Z2 two-step process.
- an upper limit is exceeded, it is switched to the idle mode.
- the limit can be set by the choice of the spring size of the relief valves 5, 6. This mode is shown in FIG. On the relief valves 5, 6 acts the pressure p3 (upper limit), so that they open and relieve the cylinder chambers 9,10.
- these can also be controlled externally pneumatically, hydraulically or electromagnetically.
- FIGS. 10 to 12 Different embodiments of compressors and their switching possibilities are shown schematically in FIGS. 10 to 12.
- the figures first show a compressor with two stages Z1, Z2 (FIG. 10), with three stages Z1, Z2, Z3 (FIG. 11) and in a further embodiment an example with n stages Z1, Z2, Z3, Zn (Fig. 12).
- n corresponds to a number from the set of numbers of the natural numbers.
- the corresponding suction chambers and pressure chambers are marked in the drawings respectively with S for suction chamber and D for pressure chamber.
- the identical numbering means that the same pressure prevails within the respective chamber because the chambers (suction chambers S and pressure chambers D) are fluidly connected to one another via already described overflow channels.
- FIG. 10 [A] shows a normal operating situation of a compressor 1 consisting of a first stage Z1 and a second stage Z2.
- the first suction chamber 1 1 sucks from the outside (shown by an arrow pointing to the first suction chamber) and compressed in the first pressure chamber 12. This in turn expands into the second suction chamber 13, which in turn compresses into the second pressure chamber 14. From this, the discharge takes place (this means that the compressed air is discharged only from the second pressure chamber 14, indicated by an arrow in Fig.
- FIG. 10 [C] An alternative switching option (FIG. 10 [C]) provides that the first suction chamber 11 and the further suction chamber 13 suck in independently of one another and compress both into the second pressure chamber 14, via which the pressure is then output.
- the compressor shown schematically in Fig. 1 1 differs from the previous embodiments in that a further stage Z3 is present.
- the compressor 1 shown here has a first stage Z1, a second stage Z2 and a third stage Z3, each stage having a suction chamber and a pressure chamber.
- the compressor 1 comprises a first suction chamber 11, a first pressure chamber 12, a second suction chamber 13 and a second pressure chamber 14, as well as a third suction chamber 20 and a fourth pressure chamber 21.
- FIG. 11 [A] A first circuit variant is shown in FIG. 11 [A]. It consists in that via the first suction chamber 1 1 is sucked in and all other suction chambers 13, 20 are fluidly connected to the first suction chamber.
- the transverse line in Fig. 11 [A] is intended to indicate this.
- This Saugkannnnern 1 1, 13, 20 compress into the other Druckkannnner, which is formed by a fluid-moderate interconnection of the first Druckkannnner 12, the second Druckkannnner 14 and the third Druckkannnner 21.
- the output takes place via the third pressure cannister 21.
- FIG. 11 [B] A further circuit variant is shown in FIG. 11 [B]. It consists in that, independently of the first suction cannister 11, the second suction cannister 13 and the third suction cannister 20 can be aspirated and each of the suction cannisters 13, 20 can be compressed into the further pressure chambers, which are connected in fluid communication between the first pressure chamber 12, the second pressure chamber 14 and the third pressure chamber 21 is formed. The output takes place via the third pressure chamber 21.
- FIG. 1 1 [C] Another circuit variant is shown in Fig. 1 1 [C]. It consists in that the second suction chamber 13 and the third suction chamber 20 are sucked in independently via the first suction chamber 11 and compress each of the suction chambers 13, 20 into the further pressure chamber, which is connected to the first pressure chamber 12, the second pressure chamber, by fluid communication 14 and the third pressure chamber 21 is formed. The output is via each of the pressure chambers 12, 14 and 21.
- FIG. 11 [D] A circuit variant shown in FIG. 11 [D] is shown in FIG. 11.
- [A] shows an embodiment in which 1 is sucked in via the first suction chamber 11 and the second suction chambers 13 are fluidly connected to the first suction chamber 11 is.
- the transverse line in Fig. 11 [D] is intended to indicate this.
- These suction chambers 1 1, 13 compress into the further pressure chamber, which is formed by a fluid-moderate interconnection of the first pressure chamber 12 and the second pressure chamber 14.
- This pressure chamber relieves pressure in the third suction chamber 20, which in turn compresses into the further third pressure chamber 21.
- the output takes place via the third pressure chamber 21.
- a circuit variant shown in Fig. 1 1 [E] is shown in Fig.
- FIG. 1 1 [A] shows an embodiment that is sucked both on the first suction chamber 1 1 and on the second suction chamber 13, wherein the second suction chambers 13 are not fluidly connected to the first suction chamber 1 1.
- These suction chambers 1 1, 13 compress into the further pressure chamber, which is formed by a fluidmassige interconnection of the first pressure chamber 12 and the second pressure chamber 14.
- This pressure chamber relieves pressure in the third suction chamber 20, which in turn compresses into the further third pressure chamber 21.
- the output takes place via the third pressure chamber 21.
- Fig. 12 [A] shows a compressor 1, which is that 1 1 is sucked on the first suction chamber and all other suction chambers 13, 20, Sn are fluidly connected to the first suction chamber.
- the transverse line in Fig. 12 [A] is intended to indicate this. In all suction chambers 1 1, 13, 20, Sn, the same pressure prevails.
- suction chambers 1 1, 13, 20, Sn compress into the further pressure chamber, by a fluidmassige interconnection of the first pressure chamber 12, the second pressure chamber 14 and the third pressure chamber 21 and the other
- Pressure chambers Dn is formed. The output is via the last pressure chamber Dn in the row.
- Fig. 12 [B] is compared with Fig. 12 [A] the variant is that each of the suction chambers 1 1, 13, 20, Sn suck for themselves and compress these suction chambers 1 1, 13, 20, Sn in the further pressure chamber , which is formed by a fluidmassige interconnection of the first pressure chamber 12, the second pressure chamber 14 and the third pressure chamber 21 and the other pressure chambers Dn.
- the output is via each of the pressure chambers 12, 14, 21 and Dn.
- the output is made via the last pressure can Dn in the row.
- a circuit variant shown in Fig. 12 [D] shows an embodiment, which is that 1 is sucked on the first suction chamber 1 and the second Saugkannnnern 13 with the first suction chamber 1 1 is fluidly connected.
- the transverse line in Fig. 12 [D] is intended to indicate this.
- These suction chambers 1 1, 13 compress into the further pressure chamber, which is formed by a fluid-moderate interconnection of the first pressure chamber 12 and the second pressure chamber 14.
- This pressure chamber relieves pressure in the third suction chamber 20, which in turn compresses into the further third pressure chamber 21.
- the third pressure chamber 21 can relieve pressure in one or more further suction chambers Sn, with the last suction chamber Sn being compressed into the last pressure chamber Sn.
- the output is via the last pressure chamber Sn.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014202265.7A DE102014202265A1 (en) | 2014-02-07 | 2014-02-07 | Compressor for a compressed air system, in particular of a motor vehicle |
PCT/EP2015/052281 WO2015118001A1 (en) | 2014-02-07 | 2015-02-04 | Compressor for a compressed air system in particular for a motor vehicle |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3102826A1 true EP3102826A1 (en) | 2016-12-14 |
Family
ID=52450112
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15702759.0A Withdrawn EP3102826A1 (en) | 2014-02-07 | 2015-02-04 | Compressor for a compressed air system in particular for a motor vehicle |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP3102826A1 (en) |
DE (1) | DE102014202265A1 (en) |
WO (1) | WO2015118001A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015225065B4 (en) * | 2015-12-14 | 2022-03-31 | Voith Patent Gmbh | Cylinder head for multi-stage piston compressor |
DE102016111100A1 (en) * | 2016-06-17 | 2017-12-21 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Valve device for increasing the performance of multistage compressor units |
DE102017205366A1 (en) * | 2017-03-29 | 2018-10-04 | Mahle International Gmbh | Multi-stage compressor |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1419221A (en) * | 1918-06-18 | 1922-06-13 | Fred S Carver | Compression pump |
GB294726A (en) * | 1927-05-16 | 1928-08-02 | William Frederick Jennings | Improvements in and relating to gas and air compressors |
DE940779C (en) * | 1950-11-16 | 1956-03-29 | Elektron Co M B H | Two-cylinder piston compressor |
US3096927A (en) * | 1959-10-13 | 1963-07-09 | Wahl Hermann | Relieving device for multiple stage compressors |
DE9007487U1 (en) * | 1990-06-29 | 1992-01-09 | Atmos Medizintechnik Gmbh & Co., 7825 Lenzkirch, De | |
US5577390A (en) * | 1994-11-14 | 1996-11-26 | Carrier Corporation | Compressor for single or multi-stage operation |
DE202004001051U1 (en) * | 2004-01-27 | 2004-04-15 | BSW Verfahrenstechnik GmbH Ingenieur- und Beratungsbüro | Multi-headed pump used as a membrane pump for producing a vacuum comprises shut-off and switching devices integrated in the suction and pressure lines between the pump heads |
DE502005002636D1 (en) | 2004-10-19 | 2008-03-13 | Voith Patent Gmbh | Multi-stage reciprocating compressor with reduced power consumption during idling |
US7353786B2 (en) * | 2006-01-07 | 2008-04-08 | Scuderi Group, Llc | Split-cycle air hybrid engine |
AT502998B1 (en) * | 2006-01-11 | 2008-05-15 | Leobersdorfer Maschf | HIGH-PRESSURE COMPRESSOR, AND ITS USE AND METHOD OF OPERATION THEREOF |
WO2008101517A1 (en) * | 2007-02-22 | 2008-08-28 | Gardner Denver Thomas Gmbh | Multiple connection pump having noise reducing valve and bearing coupling |
DE102009011214A1 (en) * | 2009-03-04 | 2010-09-23 | Technische Universität Dresden | piston compressor |
-
2014
- 2014-02-07 DE DE102014202265.7A patent/DE102014202265A1/en not_active Withdrawn
-
2015
- 2015-02-04 WO PCT/EP2015/052281 patent/WO2015118001A1/en active Application Filing
- 2015-02-04 EP EP15702759.0A patent/EP3102826A1/en not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO2015118001A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102014202265A1 (en) | 2015-08-13 |
WO2015118001A1 (en) | 2015-08-13 |
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