EP1789681B1 - Piston compressor producing an internal cooling air flow in the crankcase - Google Patents
Piston compressor producing an internal cooling air flow in the crankcase Download PDFInfo
- Publication number
- EP1789681B1 EP1789681B1 EP05778871A EP05778871A EP1789681B1 EP 1789681 B1 EP1789681 B1 EP 1789681B1 EP 05778871 A EP05778871 A EP 05778871A EP 05778871 A EP05778871 A EP 05778871A EP 1789681 B1 EP1789681 B1 EP 1789681B1
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- EP
- European Patent Office
- Prior art keywords
- crankcase
- cooling air
- cylinder head
- cylinder
- cooling
- 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.)
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- 238000001816 cooling Methods 0.000 title claims abstract description 108
- 238000007789 sealing Methods 0.000 claims description 9
- 238000010438 heat treatment Methods 0.000 claims description 7
- 230000000694 effects Effects 0.000 claims description 6
- 230000007704 transition Effects 0.000 claims description 3
- 230000032258 transport Effects 0.000 abstract 1
- 239000003570 air Substances 0.000 description 93
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 9
- 238000005096 rolling process Methods 0.000 description 8
- 230000008901 benefit Effects 0.000 description 5
- 239000012535 impurity Substances 0.000 description 4
- 230000017525 heat dissipation Effects 0.000 description 3
- 238000012423 maintenance Methods 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000035508 accumulation Effects 0.000 description 2
- 238000009825 accumulation Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 239000000725 suspension Substances 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- 229910001369 Brass Inorganic materials 0.000 description 1
- 241000446313 Lamella Species 0.000 description 1
- 230000032683 aging Effects 0.000 description 1
- 239000012080 ambient air Substances 0.000 description 1
- 239000010951 brass Substances 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000012459 cleaning agent Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 230000037406 food intake Effects 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000005226 mechanical processes and functions Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 239000003507 refrigerant Substances 0.000 description 1
Images
Classifications
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- 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
- F04B39/06—Cooling; Heating; Prevention of freezing
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- 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
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- 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
- F04B39/121—Casings
Definitions
- the invention relates to a reciprocating compressor, in particular a reciprocating compressor for generating compressed air, which comprises at least one piston connected to a roller bearing with a crankshaft connected to a roller bearing which performs a lifting movement in an associated cylinder and the compression of a connection unit integrated in the cylinder head
- Intake air causes, via an inlet valve due to a generated by the piston movement negative pressure in the crankcase cooling air from the intake into the crankcase and escapes due to the overpressure generated in the crankcase via an exhaust valve from the crankcase and thus an internal cooling air flow in the crankcase can be generated ,
- Such reciprocating compressors are usually used wherever compressed air is needed, but the compressed air generating unit must be space-saving and thus small-sized while having high power densities, which are mainly used in commercial vehicles or rail vehicles such reciprocating compressors.
- the compressed air generated by the piston compressor is increasingly used in addition to the operation of the brake system for the operation of the air suspension system.
- the high pressures required by the air suspension within short intervals of time can be generated with such reciprocating compressors.
- oil-lubricated reciprocating compressors were used in commercial vehicles in particular, oil-free compressor concepts could not prevail because the necessary component service life could not be achieved due to the high component temperatures resulting from the high power density in the smallest possible space.
- Novel compressor concepts based on reciprocating compressors allow oil-free operation if they are provided with a cooling air flow rate.
- the oil-free operating mode was developed especially for maintenance and environmental reasons.
- the prior art shows various concepts, wherein active cooling components such as fan means are used for heat dissipation.
- the DD 238 645 A1 discloses a solution in which the air moved by a fan air flows through both the compressor unit and the drive motor.
- a disadvantage of this variant is in addition to the noise of the contaminated outdoor air, which is passed through the crankcase, which can be deposited impurities and can also form accumulations of water in the crankcase due to the pressure changes.
- an external filter system and possibly a Wasserabscheidesystem is required, which, however, increases the maintenance and service intervals shortened.
- the DE 101 38 070 C2 shows a reciprocating compressor according to the preamble of claim 1, wherein the periodic pressure fluctuation generated in the crankcase by the lifting movement of the working piston via a valve pairing is used to generate a cooling air flow in the crankcase.
- an inlet valve opens when the piston performs the lifting movement in the direction of the cylinder head and increases the volume of the crankcase, because the resulting negative pressure air flows through the inlet valve into the crankcase.
- the downward movement creates an overpressure in the crankcase and a remote from the inlet valve outlet valve opens.
- the possibility is further used to remove the cooling air of the intake to make even for the cooling air flow of the crankcase already purified air available.
- the intake air is freed of impurities by upstream cleaning agents, which occupies an essential position especially in commercial vehicle construction, since the operating environment is usually heavily polluted.
- upstream cleaning agents which occupies an essential position especially in commercial vehicle construction, since the operating environment is usually heavily polluted.
- the dew point of the water vapor contained in the air can be reached, which causes a condensation of the water vapor and thus water formation in the system.
- isolated water separators may be upstream of the compressor means. In a tap of the cooling air from the intake pipe with an addition to the filter system upstream water separator is also ensured that when flowing through the filtered and dried cooling air through the crankcase there can form no amounts of water that would cause considerable damage, in particular to the bearings.
- the principle of the internal pump for cooling air promotion based on the piston movement, can be used because the low pressure stage has a large piston area and the high pressure stage via a small piston area, which also over the crank stroke due to the piston surface difference also a periodically changing pressure curve in the Crankcase is created.
- a refrigerant compressor which comprises a motor unit and a compressor unit. Cooling air is supplied to the compressor housing via a suction gas pipe and a shut-off valve, with part of this cooling air being conducted via the engine unit, while the remaining part of the cooling air passes directly into the compressor unit. The cooling air used for cooling the engine is then also led to the compressor unit.
- a disadvantage of such a design is that the cooling air routed via the engine is also heated to a high degree, and therefore, in the following, sufficient cooling of the roller bearings in the crankcase is no longer possible.
- crankcase ventilation for an oil-free piston compressor which conveys a clean cooling air into the crankcase for cooling thermally stressed components in the crankcase, in particular rolling bearings, and which has a low temperature on entry into the crankcase ,
- the invention includes the technical teaching that the diversion of the cooling air from the intake pipe itself or in the cylinder head is arranged and the cooling air via at least one outside of the cylinder passing pipe connection between the cylinder head and the crankcase is adopted to prevent heating of the cooling air ,
- This solution has the advantage of not exposing the cooling air to the heat generated in the area of the connection unit, but to branch off the intake line away from this heat source and lead directly into the crankcase.
- the previously known solution which initially leads the cooling air through channels on the lateral surface of the cylinder, causes a heating of the cooling air, even before it reaches the crankcase.
- the cooling of the Cylinder and the cylinder head can be carried out in the inventive solution by a second, separate cooling air flow, so that must not be waived cooling of these components.
- the pipe connection is arranged on the outside of the housing and passes the cooling air to the components with the highest temperatures, such as cylinder and cylinder head. Due to the freely arranged pipe connection, the temperature of the cooling air can also be further reduced via a heat dissipation based on convection via the pipe surface, before it enters the crankcase.
- Another measure improving the invention provides that the guided over the at least one pipe joint cooling air at a point in the crankcase is introduced, in the vicinity of the thermally loaded components such as the rolling bearings are arranged in the crankcase and the cooling air flows through the crankcase (2) diagonally to achieve maximum cooling effect. Due to the variable design of the pipe connection, it is possible to choose the entry point of the cooling air into the crankcase so that the components to be cooled are located directly in the cooling air flow. This advantage can be applied precisely in the case of the roller bearings, which are arranged fixedly in the crankcase, such as the crankshaft bearing in the crankcase, in that the cooling air flows directly against the roller bearings and cools them.
- connection for the cooling air between the cylinder head and the crankcase consists of at least two individually arranged and mutually parallel pipe connections to increase the available pipe surface for cooling.
- the advantage of the arrangement of at least two pipe connections is in addition to the enlarged surface for convection cooling also the possibility to arrange the pipe connections so symmetrical that the entry points of the cooling air supply both the engine side and the end arranged in the crankcase bearings of the crankshaft with cooling air directly.
- the cooling air is guided from a cooling air chamber in the cylinder head into the pipe joint, wherein the cooling air chamber is filled via the inlet valve with cooling air and distributes it to the pipe joints. In general, it is sufficient if two pipe connections are provided.
- An advantage of a lamella valve is the low design complexity and high reliability. Due to the small footprint and the flat design of a louver valve, this can be optimally integrated in the cooling air chamber of the cylinder head or in the valve plate, adjacent to the main inlet valve of the compressor.
- a screw means of the crankcase, cylinder and cylinder head consists of at least one tie rod extending through the pipe joint or a screw means of crankcase, cylinder and cylinder head consists of the pipe joint.
- the number of items can be reduced by the pipe connection in addition to the cooling air flow also fulfills the mechanical function of the screw.
- a separate screw connection of the crankcase, cylinder and cylinder head can be omitted and the pipe connections are clamped mechanically with the tie rods, with the bracing additionally a sealing effect between the pipe joint and the crankcase or the cylinder head can be achieved because the pipe connection is pressure-loaded by the tension in the longitudinal direction.
- this is mechanically clamped such that both the mechanical tensile forces are absorbed and the function of the cooling air guide can be adopted and thus the number of individual parts can be reduced.
- the transition from the pipe joint to the crankcase and the cylinder head has at least one sealing element in order to avoid leaks.
- This sealing element can be made of a plastic-based O-ring consist of or be made of a comparable sealing element such as a brass sealing ring, as this is given a higher thermal stability and improved aging resistance.
- An additional measure to further improve the cooling of the entire reciprocating compressor is that the cooling air passes before entering the pipe connection via at least one flow channel within the cylinder head and / or the cylinder and causes cooling, wherein the temperature of the cooling air in the subsequent flow through the pipe connection
- an active cooling unit or based on convection cooling is again reduced and that the pipe joint on the lateral surface has heat sinks to enhance the heat dissipation by convection.
- This principle of intercooling allows the entry of low temperature cooling air into the crankcase, although previously the thermally stressed region of the cylinder and the cylinder head is previously cooled with the same cooling air.
- the flow channel not shown in the cylinder jacket and / or in the cylinder head thereby passes the cooling air past the thermally loaded components and is then guided into the pipe joint.
- heat sinks are provided on the outside of the pipe connection in order thereby to increase the surface area and to enhance the effect of the convection cooling. Cooling by active cooling media is also applicable, but they require additional design effort.
- a cross section through a reciprocating compressor with a laterally arranged pipe connection A cross section through a reciprocating compressor with a laterally arranged pipe connection.
- the reciprocating compressor 1 shown in the figure consists of a crankcase 2, a cylinder 3 and a cylinder head 4, which is composed of a valve plate 5 and a connection unit 6.
- a piston 7 carries out a lifting movement, which is generated via a crankshaft 8 and a connecting rod 9 arranged as a connection.
- the air located in the cylinder 3 is drawn by the downward movement of the piston 7 in the cylinder 3 and compressed during the upward movement of the piston 7.
- the terminal unit 6 has a main inlet valve and a main outlet valve in addition to a suction line 11 and an outlet line 12, wherein the main inlet valve is in the downward position of the piston 7 in its open position and air from the intake pipe 11 moves into the cylinder 3 and closes in the upward movement.
- the main exhaust valve is during the downward movement of the piston 7 in the closed position, and opens in the upward movement of the piston 7, whereby the thus compressed air is led out of the cylinder 3 via the output line 12 and an external consumer feeds.
- the cylinder 3 is detachably connected via a screw 18 with the crankcase 2.
- the crankshaft 8 is rotatably supported by rolling bearings 10 in the crankcase 2, wherein the connecting rod 9 is also rotatably mounted on roller bearings 10 'on the cranked portion of the crankshaft 8.
- sealing elements 17 are arranged such that they seal the transitions of the pipe joint 15 to valve plate 5 and crankcase 2 and prevent an air side stream and thus the ingress of impurities.
- cooling air thus flows directly into the crankcase and leaves it again via the outlet valve 14 when the piston 7 in the cylinder 3 makes a downward movement and thus causes an overpressure in the crankcase 2.
- the rolling bearings 10 in the crankcase 2 are directly cooled by the incoming cooling air, wherein the cooling air is introduced in a manner not shown here with two symmetrically arranged pipe joints 15 in such a way in the crankcase 2, that the rolling bearings 10 are directly flowed with cooling air.
- the roller bearing 10 'between the crankshaft 8 and the connecting rod 9 also undergoes cooling through contact with the cooling air in the crankcase 2.
- the exhaust valve 14 is disposed on the bottom side of the crankcase 2 to remove any impurities and water accumulations from the crankcase 2 and to minimize the burden of external contamination due to the bottom-side arrangement.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
Description
Die Erfindung betrifft einen Kolbenkompressor, insbesondere einen Hubkolbenkompressor zur Erzeugung von Druckluft, welcher mindestens einen über eine zugeordnete mit einer Wälzlagerung gelagerte Pleuel mit einer Kurbelwelle verbundenen Kolben umfasst, der in einem zugeordneten Zylinder eine Hubbewegung ausführt und über eine im Zylinderkopf integrierte Anschlusseinheit die Verdichtung von Ansaugluft bewirkt, wobei über ein Einlassventil aufgrund eines durch die Kolbenbewegung erzeugten Unterdruckes im Kurbelgehäuse Kühlluft aus der Ansaugleitung in das Kurbelgehäuse gelangt und aufgrund des über die Kolbenrückbewegung erzeugten Überdruckes im Kurbelgehäuse über ein Auslassventil aus dem Kurbelgehäuse entweicht und somit ein interner Kühlluftstrom im Kurbelgehäuse erzeugbar ist.The invention relates to a reciprocating compressor, in particular a reciprocating compressor for generating compressed air, which comprises at least one piston connected to a roller bearing with a crankshaft connected to a roller bearing which performs a lifting movement in an associated cylinder and the compression of a connection unit integrated in the cylinder head Intake air causes, via an inlet valve due to a generated by the piston movement negative pressure in the crankcase cooling air from the intake into the crankcase and escapes due to the overpressure generated in the crankcase via an exhaust valve from the crankcase and thus an internal cooling air flow in the crankcase can be generated ,
Derartige Kolbenkompressoren kommen üblicherweise überall dort zum Einsatz, wo Druckluft benötigt wird, jedoch die drucklufterzeugende Einheit platzsparend und damit kleinbauend sein muss und dabei hohe Leistungsdichten aufweist, womit derartige Kolbenkompressoren hauptsächlich in Nutzfahrzeugen oder Schienenfahrzeugen genutzt werden. Im Falle des Einsatzes im Nutzfahrzeug wird in zunehmendem Maße die durch den Kolbenkompressor erzeugte Druckluft neben dem Betrieb der Bremsanlage auch zum Betrieb der Luftfederungsanlage genutzt. Wegen des damit einhergehenden großen Druckluftbedarfs mit hohen Systemdrücken eignen sich hier meist mehrstufige Kolbenkompressoren. Die durch die innerhalb kurzer Zeitintervalle für die Luftfederung erforderlichen hohen Drücke sind mit derartigen Kolbenkompressoren erzeugbar. Dabei kamen insbesondere in der Vergangenheit in Nutzfahrzeugen ölgeschmierte Kolbenkompressoren zum Einsatz, ölfreie Verdichterkonzepte konnten sich nicht durchsetzen, da aufgrund der hohen Bauteiltemperaturen, die aus der hohen Leistungsdichte auf kleinstem Bauraum resultieren, die nötigen Bauteilstandzeiten nicht erreicht werden konnten.Such reciprocating compressors are usually used wherever compressed air is needed, but the compressed air generating unit must be space-saving and thus small-sized while having high power densities, which are mainly used in commercial vehicles or rail vehicles such reciprocating compressors. In the case of use in commercial vehicles, the compressed air generated by the piston compressor is increasingly used in addition to the operation of the brake system for the operation of the air suspension system. Because of the associated large compressed air demand with high system pressures here are mostly multi-stage reciprocating compressors. The high pressures required by the air suspension within short intervals of time can be generated with such reciprocating compressors. In the past, oil-lubricated reciprocating compressors were used in commercial vehicles in particular, oil-free compressor concepts could not prevail because the necessary component service life could not be achieved due to the high component temperatures resulting from the high power density in the smallest possible space.
Neuartige Verdichterkonzepte auf Basis von Kolbenkompressoren lassen einen ölfreien Betrieb zu, wenn diese mit einem Kühlluftdurchsatz versehen werden. Die ölfreie Betriebsart wurde insbesondere aus wartungs- und umwelttechnischen Gründen entwickelt. Hier zeigt der Stand der Technik verschiedene Konzepte, wobei aktive Kühlkomponenten wie beispielsweise Lüftermittel für eine Wärmeabfuhr eingesetzt werden.Novel compressor concepts based on reciprocating compressors allow oil-free operation if they are provided with a cooling air flow rate. The oil-free operating mode was developed especially for maintenance and environmental reasons. Here, the prior art shows various concepts, wherein active cooling components such as fan means are used for heat dissipation.
Die
Die
Um das Einlassen von verunreinigter Umgebungsluft zu vermeiden, wird weiterführend die Möglichkeit genutzt, die Kühlluft der Ansaugleitung zu entnehmen, um auch für den Kühlluftstrom des Kurbelgehäuses bereits gereinigte Luft zur Verfügung zu stellen. Die Ansaugluft ist durch vorgelagerte Reinigungsmittel von Verunreinigungen befreit, was insbesondere im Nutzfahrzeugbau eine wesentliche Stellung einnimmt, da die Betriebsumgebung meist stark staubbelastet ist. Weiterhin kann bei Vorrichtungen, die zur Druckluftaufbereitung starke Druckänderungen in der Arbeitsluft hervorrufen, der Taupunkt des in der Luft enthaltenen Wasserdampfes erreicht werden, was eine Kondensierung des Wasserdampfes und damit Wasserbildung im System verursacht. Um die Wasserbildung im System zu vermeiden, können vereinzelt Wasserabscheider den Verdichtermitteln vorgeschaltet sein. Bei einem Abgriff der Kühlluft von der Ansaugleitung mit einem zusätzlich zum Filtersystem vorgeschalteten Wasserabscheider ist zudem sichergestellt, dass sich bei einem Durchströmen der gefilterten und getrockneten Kühlluft durch das Kurbelgehäuse dort keine Wassermengen bilden können, die erhebliche Schäden insbesondere an den Lagerungen hervorrufen würden.In order to avoid the ingestion of contaminated ambient air, the possibility is further used to remove the cooling air of the intake to make even for the cooling air flow of the crankcase already purified air available. The intake air is freed of impurities by upstream cleaning agents, which occupies an essential position especially in commercial vehicle construction, since the operating environment is usually heavily polluted. Furthermore, in devices that are used for Compressed air treatment causes strong pressure changes in the working air, the dew point of the water vapor contained in the air can be reached, which causes a condensation of the water vapor and thus water formation in the system. In order to avoid the formation of water in the system, isolated water separators may be upstream of the compressor means. In a tap of the cooling air from the intake pipe with an addition to the filter system upstream water separator is also ensured that when flowing through the filtered and dried cooling air through the crankcase there can form no amounts of water that would cause considerable damage, in particular to the bearings.
Auch bei mehrstufigen Kolbenkompressoren, wie aus der
Jedoch ergibt sich dabei das Problem, dass sich bei einem Abzweig der Kühlluft von der Ansaugleitung durch die Position des Abzweigs im Zylinderkopf oder nahe des Zylinderkopfes und ein direktes Einleiten der Kühlluft über ein im Zylinderkopf befindliches Einlassventil und anschließendes Vorbeiführen der Kühlluft am Zylinder die Kühlluft derart erwärmt, dass zur Kühlung der Wälzlager im Kurbelgehäuse keine Kühlluft entsprechend niedriger Temperatur mehr zur Verfügung steht. Durch die damit verursachten hohen Betriebstemperaturen insbesondere der Wälzlagerungen ist die Lebensdauer ölfreier Kolbenkompressoren erheblich eingeschränkt, was mit verkürzten Wartungsintervallen verbunden ist und Betriebsausfälle verursachen kann. Die Fettschmierung der Wälzlager altert durch Zersetzungsprozesse bei hohen Betriebstemperaturen, für die meisten Fette gelten Temperaturgrenzen von 90°C, die bei einem Betrieb des Kompressors schon nach kurzer Dauer erreichet werden können. Dadurch ist eine zuverlässige Schmierwirkung nicht mehr sichergestellt, was zu einem Ausfall der Wälzlagerung führt.However, this results in the problem that at a branch of the cooling air from the intake pipe through the position of the branch in the cylinder head or near the cylinder head and a direct introduction of the cooling air via an intake valve located in the cylinder head and then passing the cooling air to the cylinder so the cooling air heats up that no cooling air corresponding low temperature is available for cooling the bearings in the crankcase. Due to the resulting high operating temperatures, in particular the rolling bearings, the life of oil-free reciprocating compressors is considerably limited, which is associated with reduced maintenance intervals and can cause business interruptions. The grease lubrication of rolling bearings ages due to decomposition processes at high operating temperatures, for most greases there are temperature limits of 90 ° C, which can be reached within a short period of time when operating the compressor. As a result, a reliable lubricating effect is no longer guaranteed, resulting in a failure of the rolling bearing.
Aus der
Nachteilhaft an einer derartigen Ausführung ist, dass die über den Motor geleitete Kühlluft ebenfalls starkt erwärmt wird und im Folgenden daher eine ausreichende Kühlung der Wälzlagerungen im Kurbelgehäuse nicht mehr möglich ist.A disadvantage of such a design is that the cooling air routed via the engine is also heated to a high degree, and therefore, in the following, sufficient cooling of the roller bearings in the crankcase is no longer possible.
Es ist daher die Aufgabe der vorliegenden Erfindung, eine Kurbelgehäusebelüftung für einen ölfreien Kolbenkompressor zu schaffen, die zur Kühlung von thermisch belasteten Komponenten im Kurbelgehäuse, insbesondere von Wälzlagerungen, eine saubere Kühlluft in das Kurbelgehäuse befördert und die beim Eintritt in das Kurbelgehäuse eine niedrige Temperatur aufweist.It is therefore the object of the present invention to provide a crankcase ventilation for an oil-free piston compressor, which conveys a clean cooling air into the crankcase for cooling thermally stressed components in the crankcase, in particular rolling bearings, and which has a low temperature on entry into the crankcase ,
Diese Aufgabe wird ausgehend von einer Kurbelgehäusebelüftung für einen ölfreien Kolbenkompressor gemäß dem Oberbegriff des Anspruchs 1 in Verbindung mit dessen kennzeichnenden Merkmalen gelöst. Vorteilhafte Weiterbildungen der Erfindung sind in den abhängigen Ansprüchen angegeben.This object is achieved on the basis of a crankcase ventilation for an oil-free piston compressor according to the preamble of
Die Erfindung schließt die technische Lehre ein, dass die Abzweigung der Kühlluft aus der Ansaugleitung selbst oder im Zylinderkopf angeordnet ist und die Kühlluft über mindestens eine außen am Zylinder vorbeiführende Rohrverbindung zwischen Zylinderkopf und dem Kurbelgehäuse am Zylinder vorbeileitbar ist, um eine Erwärmung der Kühlluft zu vermeiden.The invention includes the technical teaching that the diversion of the cooling air from the intake pipe itself or in the cylinder head is arranged and the cooling air via at least one outside of the cylinder passing pipe connection between the cylinder head and the crankcase is vorbeileitbar on the cylinder to prevent heating of the cooling air ,
Diese Lösung bietet den Vorteil, die Kühlluft nicht der Wärme auszusetzen, die im Bereich der Anschlusseinheit entsteht, sondern fern von dieser Wärmequelle von der Ansaugleitung abzuzweigen und direkt in das Kurbelgehäuse zu leiten. Die vorbekannte Lösung, die die Kühlluft zunächst über Kanäle an der Mantelfläche des Zylinders entlang führt, bedingt ein Aufheizen der Kühlluft, noch bevor diese das Kurbelwellengehäuse erreicht. Die Kühlung des Zylinders und des Zylinderkopfes kann bei der erfindungsgemäßen Lösung auch durch einen zweiten, separaten Kühlluftstrom erfolgen, so dass auf eine Kühlung dieser Komponenten nicht verzichtet werden muss. So kann eine vor dem Eintritt in das Kurbelgehäuse stattfindende Erwärmung der Kühlluft einfach vermieden werden. Die Rohrverbindung ist außen am Gehäuse angeordnet und leitet die Kühlluft an den Bauteilen mit den höchsten Temperaturen wie Zylinder und Zylinderkopf, vorbei. Durch die frei angeordnete Rohrverbindung kann die Temperatur der Kühlluft über eine auf Konvektion über die Rohroberfläche beruhende Wärmeabfuhr zudem weiter reduziert werden, bevor diese in das Kurbelgehäuse eintritt.This solution has the advantage of not exposing the cooling air to the heat generated in the area of the connection unit, but to branch off the intake line away from this heat source and lead directly into the crankcase. The previously known solution, which initially leads the cooling air through channels on the lateral surface of the cylinder, causes a heating of the cooling air, even before it reaches the crankcase. The cooling of the Cylinder and the cylinder head can be carried out in the inventive solution by a second, separate cooling air flow, so that must not be waived cooling of these components. Thus, a heating of the cooling air taking place before entering the crankcase can be easily avoided. The pipe connection is arranged on the outside of the housing and passes the cooling air to the components with the highest temperatures, such as cylinder and cylinder head. Due to the freely arranged pipe connection, the temperature of the cooling air can also be further reduced via a heat dissipation based on convection via the pipe surface, before it enters the crankcase.
Eine weitere die Erfindung verbessernde Maßnahme sieht vor, dass die über die mindestens eine Rohrverbindung geführte Kühlluft an einer Stelle ins Kurbelgehäuse einleitbar ist, in deren Nähe die thermisch belasteten Komponenten wie die Wälzlagerungen im Kurbelgehäuse angeordnet sind und die Kühlluft das Kurbelgehäuse (2) diagonal durchströmt, um eine maximale Kühlwirkung zu erzielen. Durch die variable Gestaltung der Rohrverbindung ist es möglich, die Eintrittsstelle der Kühlluft in das Kurbelgehäuse so zu wählen, dass sich die zu kühlenden Komponenten direkt im Kühlluftstrom befinden. Dieser Vorteil kann gerade bei den ortsfest im Kurbelgehäuse angeordneten Wälzlagern, wie der Kurbelwellenlagerung im Kurbelgehäuse, angewendet werden, indem die Kühlluft direkt die Wälzlagerungen anströmt und diese kühlt.Another measure improving the invention provides that the guided over the at least one pipe joint cooling air at a point in the crankcase is introduced, in the vicinity of the thermally loaded components such as the rolling bearings are arranged in the crankcase and the cooling air flows through the crankcase (2) diagonally to achieve maximum cooling effect. Due to the variable design of the pipe connection, it is possible to choose the entry point of the cooling air into the crankcase so that the components to be cooled are located directly in the cooling air flow. This advantage can be applied precisely in the case of the roller bearings, which are arranged fixedly in the crankcase, such as the crankshaft bearing in the crankcase, in that the cooling air flows directly against the roller bearings and cools them.
Nach einer möglichen Weiterbildung der Erfindung wird vorgeschlagen, dass die Verbindung für die Kühlluft zwischen dem Zylinderkopf und dem Kurbelgehäuse aus mindestens zwei einzeln angeordneten und zueinander parallel geschalteten Rohrverbindungen besteht, um die verfügbare Rohroberfläche zur Kühlung zu vergrößern. Der Vorteil der Anordnung von mindestens zwei Rohrverbindungen ist neben der vergrößerten Oberfläche zur Konvektionskühlung zudem die Möglichkeit, die Rohrverbindungen derart symmetrisch anzuordnen, dass die Eintrittsstellen der Kühlluft sowohl das motorseitig als auch das endseitig im Kurbelgehäuse angeordnete Wälzlager der Kurbelwelle mit Kühlluft direkt versorgen. Die Kühlluft wird dabei aus einer Kühlluftkammer im Zylinderkopf in die Rohrverbindung geführt, wobei die Kühlluftkammer über das Einlassventil mit Kühlluft gefüllt wird und diese auf die Rohrverbindungen verteilt. In der Regel ist es ausreichend, wenn zwei Rohrverbindungen vorgesehen werden.According to a possible development of the invention, it is proposed that the connection for the cooling air between the cylinder head and the crankcase consists of at least two individually arranged and mutually parallel pipe connections to increase the available pipe surface for cooling. The advantage of the arrangement of at least two pipe connections is in addition to the enlarged surface for convection cooling also the possibility to arrange the pipe connections so symmetrical that the entry points of the cooling air supply both the engine side and the end arranged in the crankcase bearings of the crankshaft with cooling air directly. The cooling air is guided from a cooling air chamber in the cylinder head into the pipe joint, wherein the cooling air chamber is filled via the inlet valve with cooling air and distributes it to the pipe joints. In general, it is sufficient if two pipe connections are provided.
Um eine betriebssichere und platzsparende Ventilanordnung zu schaffen, wird als weitere die Erfindung verbessernde Maßnahme vorgeschlagen, das Einlassventil und/oder das Auslassventil für den Kühlluftstrom nach Art eines Lamellenventils auszubilden und das Einlassventil im Zylinderkopf, in einer Ventilplatte oder im Kurbelgehäuse anzuordnen. Vorteilhaft bei einem Lamellenventil ist der geringe konstruktive Aufwand und die hohe Betriebssicherheit. Aufgrund des geringen Platzbedarfs und der flachen Bauweise eines Lamellenventils lässt sich dieses optimal in der Kühlluftkammer des Zylinderkopfes oder in der Ventilplatte integrieren, und zwar benachbart zum Haupteinlassventil des Kompressors.To provide a reliable and space-saving valve assembly is proposed as a further measure improving the invention, the inlet valve and / or the outlet valve for the cooling air flow in the manner of a lamellae valve and to arrange the intake valve in the cylinder head, in a valve plate or in the crankcase. An advantage of a lamella valve is the low design complexity and high reliability. Due to the small footprint and the flat design of a louver valve, this can be optimally integrated in the cooling air chamber of the cylinder head or in the valve plate, adjacent to the main inlet valve of the compressor.
Um mit einer weiteren Maßnahme eine Erwärmung der Kühlluft zu minimieren, wird vorgeschlagen, das Einlassventil im Zylinderkopf fern vom Ort der Anschlusseinheit anzuordnen. Mit einer möglichst distalen Anordnung des Einlassventils und damit des Strömungsverlaufs der Kühlluft nach der Abzweigung aus der Ansaugleitung wird die Erwärmung der Kühlluft minimiert und auf dem direkten Weg in das Kurbelwellengehäuse geführt. Eine Abzweigung der Kühlluft außerhalb des Zylinderkopfes bzw. der Ventilplatte bietet ebenfalls eine weitere Lösung, jedoch ist dabei zusätzlich ein Abzweigelement in der Ansaugleitung erforderlich und das Einlassventil muss am Kühllufteingang des Kurbelgehäuses angeordnet sein. Diese Lösung wäre jedoch nur bei der Anwendung von einer Rohrverbindung sinnvoll, da bei einer Kühlluftführung über mehrere Rohre entsprechend der Anzahl der Rohrverbindungen auch mehrere Einlassventile erforderlich wären.In order to minimize a heating of the cooling air with a further measure, it is proposed to arrange the inlet valve in the cylinder head far from the location of the connection unit. With a distal possible arrangement of the inlet valve and thus the flow of the cooling air after the branch from the intake manifold, the heating of the cooling air is minimized and performed on the direct path in the crankcase. A diversion of the cooling air outside of the cylinder head or the valve plate also provides another solution, but in addition a branch element in the intake manifold is required and the inlet valve must be located at the cooling air inlet of the crankcase. However, this solution would be useful only in the application of a pipe connection, as in a cooling air flow over several pipes according to the number of pipe connections and multiple inlet valves would be required.
Es ist aus konstruktiven Gründen von besonderem Vorteil, wenn ein Verschraubungsmittel von Kurbelgehäuse, Zylinder und Zylinderkopf aus mindestens einem Zuganker besteht, der durch die Rohrverbindung verläuft oder ein Verschraubungsmittel von Kurbelgehäuse, Zylinder und Zylinderkopf aus der Rohrverbindung besteht. Mit beiden Maßnahmen kann die Anzahl der Einzelteile reduziert werden, indem die Rohrverbindung neben der Kühlluftführung auch die mechanische Funktion der Verschraubung erfüllt. Im Falle einer Durchführung von Zugankern durch die Rohrverbindung kann eine separate Verschraubung von Kurbelgehäuse, Zylinder und Zylinderkopf entfallen und die Rohrverbindungen werden mit den Zugankern mechanisch verspannt, wobei mit der Verspannung zusätzlich eine Dichtwirkung zwischen der Rohrverbindung und dem Kurbelgehäuse bzw. dem Zylinderkopf erreicht werden kann, da die Rohrverbindung durch die Verspannung in Längsrichtung druckbelastet ist. Bei einer Verschraubung von Kurbelgehäuse, Zylinder und Zylinderkopf über die Rohrverbindung ist diese derart mechanisch verspannt, dass sowohl die mechanischen Zugkräfte aufgenommen werden als auch die Funktion der Kühlluftführung übernommen werden kann und somit die Anzahl von Einzelteilen reduzierbar ist.It is for structural reasons of particular advantage, when a screw means of the crankcase, cylinder and cylinder head consists of at least one tie rod extending through the pipe joint or a screw means of crankcase, cylinder and cylinder head consists of the pipe joint. With both measures, the number of items can be reduced by the pipe connection in addition to the cooling air flow also fulfills the mechanical function of the screw. In the case of a passage of tie rods through the pipe joint, a separate screw connection of the crankcase, cylinder and cylinder head can be omitted and the pipe connections are clamped mechanically with the tie rods, with the bracing additionally a sealing effect between the pipe joint and the crankcase or the cylinder head can be achieved because the pipe connection is pressure-loaded by the tension in the longitudinal direction. In a screw connection of the crankcase, cylinder and cylinder head via the pipe connection, this is mechanically clamped such that both the mechanical tensile forces are absorbed and the function of the cooling air guide can be adopted and thus the number of individual parts can be reduced.
Um eine Dichtwirkung zwischen der Rohrverbindung und dem Kurbelgehäuse bzw. dem Zylinderkopf zu erreichen, wird vorgeschlagen, dass der Übergang von der Rohrverbindung zum Kurbelgehäuse und zum Zylinderkopf mindestens ein Dichtelement aufweist, um Leckagen zu vermeiden. Dieses Dichtelement kann aus einem O-Ring auf Kunststoffbasis bestehen oder aus einem vergleichbaren Dichtelement wie beispielsweise eines Messingdichtrings hergestellt sein, da damit eine höhere thermische Stabilität und eine verbesserte Alterungsbeständigkeit gegeben ist.In order to achieve a sealing effect between the pipe joint and the crankcase or the cylinder head, it is proposed that the transition from the pipe joint to the crankcase and the cylinder head has at least one sealing element in order to avoid leaks. This sealing element can be made of a plastic-based O-ring consist of or be made of a comparable sealing element such as a brass sealing ring, as this is given a higher thermal stability and improved aging resistance.
Eine zusätzliche Maßnahme zur weiteren Verbesserung der Kühlung des gesamten Hubkolbenkompressors besteht darin, dass die Kühlluft vor Eintritt in die Rohrverbindung über mindestens einen Strömungskanal innerhalb des Zylinderkopfes und/oder des Zylinders verläuft und eine Kühlung bewirkt, wobei die Temperatur der Kühlluft beim nachfolgenden Durchströmen der Rohrverbindung insbesondere durch eine aktive Kühleinheit oder beruhend auf Konvektionskühlung wieder reduzierbar ist und dass die Rohrverbindung auf der Mantelfläche Kühlkörper aufweist, um die Wärmeabfuhr durch Konvektion zu verstärken. Dieses Prinzip der Zwischenkühlung ermöglicht den Eintritt von Kühlluft niedriger Temperatur in das Kurbelgehäuse, obwohl zuvor der thermisch stark beanspruchte Bereich des Zylinders und des Zylinderkopfes mit der gleichen Kühlluft vorab gekühlt wird. Der nicht näher dargestellte Strömungskanal im Zylindermantel und/ oder im Zylinderkopf leitet dabei die Kühlluft an den thermisch belasteten Bauteilen vorbei und wird dann in die Rohrverbindung geführt. Um die Temperatur der Kühlluft wieder hinreichend zu reduzieren, so dass diese bei Eintritt in das Kurbelgehäuse eine effektive Kühlung der Wälzlagerungen bewirkt, sind erfindungsgemäß Kühlkörper an der Außenseite der Rohrverbindung vorzusehen, um dadurch die Oberfläche zu vergrößern und den Effekt der Konvektionskühlung zu verstärken. Eine Kühlung durch aktive Kühlmedien ist ebenfalls anwendbar, jedoch erfordern diese einen zusätzlichen konstruktiven Aufwand.An additional measure to further improve the cooling of the entire reciprocating compressor is that the cooling air passes before entering the pipe connection via at least one flow channel within the cylinder head and / or the cylinder and causes cooling, wherein the temperature of the cooling air in the subsequent flow through the pipe connection In particular, by an active cooling unit or based on convection cooling is again reduced and that the pipe joint on the lateral surface has heat sinks to enhance the heat dissipation by convection. This principle of intercooling allows the entry of low temperature cooling air into the crankcase, although previously the thermally stressed region of the cylinder and the cylinder head is previously cooled with the same cooling air. The flow channel not shown in the cylinder jacket and / or in the cylinder head thereby passes the cooling air past the thermally loaded components and is then guided into the pipe joint. In order to sufficiently reduce the temperature of the cooling air again so that it causes effective cooling of the roller bearings when it enters the crankcase, according to the invention heat sinks are provided on the outside of the pipe connection in order thereby to increase the surface area and to enhance the effect of the convection cooling. Cooling by active cooling media is also applicable, but they require additional design effort.
Weitere die Erfindung verbessernde Maßnahmen sind in den Unteransprüchen angegeben oder werden nachstehend gemeinsam mit der Beschreibung eines bevorzugten Ausführungsbeispieles der Erfindung anhand einer Figur näher dargestellt. Die einzige Figur zeigt:Further measures improving the invention are specified in the subclaims or will be described in more detail below together with the description of a preferred embodiment of the invention with reference to a figure. The only figure shows:
Einen Querschnitt durch einen Hubkolbenkompressor mit einer seitlich angeordneten Rohrverbindung.A cross section through a reciprocating compressor with a laterally arranged pipe connection.
Der in der Figur dargestellte Hubkolbenkompressor 1 besteht aus einem Kurbelgehäuse 2, einem Zylinder 3 und einem Zylinderkopf 4, der aus einer Ventilplatte 5 und einer Anschlusseinheit 6 aufgebaut ist. Im Zylinder 3 führt ein Kolben 7 eine Hubbewegung aus, die über eine Kurbelwelle 8 und einer als Verbindung angeordneten Pleuel 9 erzeugt wird. Die sich im Zylinder 3 befindliche Luft wird durch die Abwärtsbewegung des Kolbens 7 in den Zylinder 3 eingezogen und bei der Aufwärtsbewegung des Kolbens 7 verdichtet. Die Anschlusseinheit 6 weist neben einer Ansaugleitung 11 und einer Ausgangsleitung 12 ein Haupteinlassventil und ein Hauptauslassventil auf, wobei sich das Haupteinlassventil bei der Abwärtsbewegung des Kolbens 7 in seiner Offenstellung befindet und Luft aus der Ansaugleitung 11 in den Zylinder 3 einzieht und bei der Aufwärtsbewegung schließt. Hingegen befindet sich das Hauptauslassventil während der Abwärtsbewegung des Kolbens 7 in der Schließstellung, und öffnet in der Aufwärtsbewegung des Kolbens 7, wodurch die damit sich verdichtende Luft aus dem Zylinder 3 über die Ausgangsleitung 12 herausgeführt und einem externen Verbraucher zuführt wird.The
Der Zylinder ist 3 über ein Verschraubungsmittel 18 mit dem Kurbelgehäuse 2 lösbar verbunden. Die Kurbelwelle 8 ist durch Wälzlager 10 drehbar im Kurbelgehäuse 2 gelagert, wobei die Pleuel 9 ebenfalls über Wälzlager 10' drehbar auf dem gekröpften Abschnitt der Kurbelwelle 8 gelagert ist.The
Durch die Hubbewegung des Kolbens 7 wird wie im Arbeitszylinder auch im Kurbelgehäuse 2 eine periodische Druckänderung hervorgerufen. Durch die Anordnung eines Einlassventils 13 und eines Auslassventils 14, durch die Luft in das Kurbelgehäuse 2 gelangen und entweichen kann, wird im Kurbelgehäuse 2 ein Luftdurchsatz hervorgerufen. Das Einlassventil 13 befindet sich innerhalb des Zylinderkopfes 4, und entnimmt die Kühlluft aufgrund des Unterdruckes im Kurbelgehäuse 2 durch die Aufwärtsbewegung des Kolbens 7 aus der Ansaugleitung 11, die durch eine Rohrverbindung 15 in das Kurbelgehäuse 2 geleitet wird. Die Rohrverbindung 15 ist im Ausführungsbeispiel zwischen der Ventilplatte 5 und dem Kurbelgehäuse 2 angeordnet, womit ein Luftkanal zwischen der Kühlluftkammer 16, in der sich die Kühlluft über das Einlassventil 13 aus der Ansaugleitung 11 sammelt, und dem Kurbelgehäuse 2 hergestellt ist. Die Kühlluft strömt somit durch die Rohrverbindung 15 in das Kurbelgehäuse 2, ohne sich an den Bauteilen hoher Temperatur wie Zylinder 3 oder Zylinderkopf 4 zu erwärmen.By the stroke movement of the
Zur Abdichtung der Rohrverbindung 15 und der Ventilplatte 5 bzw. dem Kurbelgehäuse 2 sind Dichtelemente 17 derart angeordnet, dass diese die Übergänge der Rohrverbindung 15 zu Ventilplatte 5 und Kurbelgehäuse 2 dichten und einen Luftnebenstrom und damit das Eindringen von Verunreinigungen verhindern. Bei geöffnetem Einlassventil 13 strömt somit Kühlluft direkt in das Kurbelgehäuse und verlässt dieses über das Auslassventil 14 wieder, wenn der Kolben 7 im Zylinder 3 eine Abwärtsbewegung ausführt und damit einen Überdruck im Kurbelgehäuse 2 hervorruft. Die Wälzlager 10 im Kurbelgehäuse 2 werden von der einströmenden Kühlluft direkt gekühlt, wobei die Kühlluft bei einer hier nicht näher dargestellten Bauweise mit zwei symmetrisch angeordneten Rohrverbindungen 15 derart in das Kurbelgehäuse 2 eingeleitet wird, dass die Wälzlager 10 direkt mit Kühlluft angeströmt werden. Zudem erfährt die Wälzlagerung 10' zwischen der Kurbelwelle 8 und der Pleuel 9 ebenfalls eine Kühlung durch den Kontakt mit der Kühlluft im Kurbelgehäuse 2.To seal the pipe joint 15 and the valve plate 5 and the
Das Auslassventil 14 ist auf der Bodenseite des Kurbelgehäuses 2 angeordnet, um eventuelle Verunreinigungen und Wasseransammlungen aus dem Kurbelgehäuse 2 herauszutransportieren und die Belastung durch Verunreinigungen von außen aufgrund der bodenseitigen Anordnung zu minimieren.The
- 11
- Hubkolbenkompressorreciprocating compressor
- 22
- Kurbelgehäusecrankcase
- 33
- Zylindercylinder
- 44
- Zylinderkopfcylinder head
- 55
- Ventilplattevalve plate
- 66
- Anschlusseinheitconnection unit
- 77
- Kolbenpiston
- 88th
- Kurbelwellecrankshaft
- 99
- Pleuelpleuel
- 10, 10'10, 10 '
- Wälzlagerungroller bearing
- 1111
- Ansaugleitungsuction
- 1212
- Ausgangsleitungoutput line
- 1313
- Einlassventilintake valve
- 1414
- Auslassventiloutlet valve
- 1515
- Rohrverbindungpipe connection
- 1616
- KühlluftkammerCooling air chamber
- 1717
- Dichtelementsealing element
- 1818
- Verschraubungsmittelscrewing
Claims (11)
- Reciprocating piston compressor (1) for producing compressed air, which comprises at least one piston (7) connected to a crankshaft (8) by an associated connecting rod (9) mounted by means of a roller bearing (10, 10'), which undergoes a reciprocating stroke movement in an associated cylinder (3) and compresses air drawn in via a connection unit (6) integrated in the cylinder head (4), such that owing to a reduced pressure in the crankcase (2) produced by the movement of the piston cooling air is drawn from the intake manifold (11) through an inlet valve (13) into the crankcase and, owing to the excess pressure in the crankcase (2) produced by the return movement of the piston the air escapes from the crankcase (2) though an outlet valve (14), so that an internal flow of cooling air can be produced in the crankcase (2),
characterised in that a cooling air branch connection is arranged in the intake manifold (11) itself or in the cylinder head (4) and the cooling air bypasses the cylinder (3) through at least one tube connection (15) that extends past the cylinder (3) on the outside thereof, between the cylinder head (4) and the crankcase (2), in order to avoid heating of the cooling air. - Piston compressor (1) according to Claim 1,
characterised in that the cooling air flowing through the at least one tube connection (15) can pass into the crankcase (2) at a point close to where the thermally stressed components, such as the roller bearings (10, 10'), are arranged in the crankcase (2), and the cooling air flows diagonally through the crankcase (2) in order to achieve the maximum cooling effect. - Piston compressor (1) according to Claims 1 or 2,
characterised in that the cooling air connection between the cylinder head (4) and the crankcase (2) consists of at least two individually arranged tube connections (15) parallel to one another, in order to provide a larger available cooling surface area. - Piston compressor (1) according to any of Claims 1 to 3,
characterised in that the inlet valve (13) and/or the outlet valve (14) is/are in the form of a lamellar valve. - Piston compressor (1) according to any of Claims 1 to 4,
characterised in that the inlet valve (13) in the cylinder head (4) is arranged in a valve plate (5) or in the crankcase (2), so that the cooling air can pass through the inlet valve (13) into the crankcase (2). - Piston compressor (1) according to any of Claims 1 to 5,
characterised in that the inlet valve (13) in the cylinder head (4) is arranged a substantial distance away from the connection unit (6), in order to minimise heating of the cooling air. - Piston compressor (1) according to any of Claims 1 to 6,
characterised in that a screw connection means (18) of the crankcase (2), cylinder (3) and cylinder head (4) consists of at least one tie-rod, which extends through the tube connection (15). - Piston compressor (1) according to any of Claims 1 to 7,
characterised in that a screw connection means (18) of the crankcase (2), cylinder (3) and cylinder head (4) consists of the tube connection (15) itself. - Piston compressor (1) according to any of Claims 1 to 8,
characterised in that the transition from the tube connection (15) to the crankcase (2) and to the cylinder head (4) comprises at least one sealing element, in order to prevent leakage. - Piston compressor (1) according to any of Claims 1 to 9,
characterised in that before passing into the tube connection (15), the cooling air passes through a flow duct within the cylinder head (4) and/or the cylinder (3), where it has a cooling effect, and when the cooling air then passes through the tube connection (15) its temperature cab be lowered again, in particular by means of an active cooling unit or by means of convective cooling. - Piston compressor (1) according to any of Claims 1 to 10,
characterised in that the tube connection (15) has cooling elements on its outer surface in order to promote the dissipation of heat by convection.
Applications Claiming Priority (2)
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DE102004042944A DE102004042944B4 (en) | 2004-09-02 | 2004-09-02 | Piston compressor with an internal cooling air flow in the crankcase |
PCT/EP2005/009367 WO2006024510A1 (en) | 2004-09-02 | 2005-08-31 | Piston compressor producing an internal cooling air flow in the crankcase |
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EP1789681A1 EP1789681A1 (en) | 2007-05-30 |
EP1789681B1 true EP1789681B1 (en) | 2009-07-29 |
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EP05778871A Active EP1789681B1 (en) | 2004-09-02 | 2005-08-31 | Piston compressor producing an internal cooling air flow in the crankcase |
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US (1) | US8308447B2 (en) |
EP (1) | EP1789681B1 (en) |
CN (1) | CN100501160C (en) |
AT (1) | ATE438036T1 (en) |
BR (1) | BRPI0514877B1 (en) |
CA (1) | CA2578843A1 (en) |
DE (2) | DE102004042944B4 (en) |
HK (1) | HK1110374A1 (en) |
MX (1) | MX2007002495A (en) |
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-
2004
- 2004-09-02 DE DE102004042944A patent/DE102004042944B4/en not_active Expired - Fee Related
-
2005
- 2005-08-31 CN CNB2005800295806A patent/CN100501160C/en active Active
- 2005-08-31 BR BRPI0514877-4A patent/BRPI0514877B1/en not_active IP Right Cessation
- 2005-08-31 US US11/574,529 patent/US8308447B2/en active Active
- 2005-08-31 WO PCT/EP2005/009367 patent/WO2006024510A1/en active Application Filing
- 2005-08-31 RU RU2007111955/06A patent/RU2362051C2/en active
- 2005-08-31 DE DE502005007800T patent/DE502005007800D1/en active Active
- 2005-08-31 AT AT05778871T patent/ATE438036T1/en active
- 2005-08-31 EP EP05778871A patent/EP1789681B1/en active Active
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- 2005-08-31 CA CA002578843A patent/CA2578843A1/en not_active Abandoned
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CA2578843A1 (en) | 2006-03-09 |
CN101010511A (en) | 2007-08-01 |
BRPI0514877B1 (en) | 2018-03-13 |
EP1789681A1 (en) | 2007-05-30 |
ATE438036T1 (en) | 2009-08-15 |
RU2362051C2 (en) | 2009-07-20 |
BRPI0514877A (en) | 2008-06-24 |
HK1110374A1 (en) | 2008-07-11 |
MX2007002495A (en) | 2007-10-10 |
DE102004042944B4 (en) | 2009-09-10 |
RU2007111955A (en) | 2008-10-10 |
WO2006024510A1 (en) | 2006-03-09 |
DE102004042944A1 (en) | 2006-03-23 |
DE502005007800D1 (en) | 2009-09-10 |
US8308447B2 (en) | 2012-11-13 |
US20070292289A1 (en) | 2007-12-20 |
CN100501160C (en) | 2009-06-17 |
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