EP2513479B1 - Coolant compressor with linear drive - Google Patents
Coolant compressor with linear drive Download PDFInfo
- Publication number
- EP2513479B1 EP2513479B1 EP10807312.3A EP10807312A EP2513479B1 EP 2513479 B1 EP2513479 B1 EP 2513479B1 EP 10807312 A EP10807312 A EP 10807312A EP 2513479 B1 EP2513479 B1 EP 2513479B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- permanent magnet
- refrigerant compressor
- valve plate
- compressor according
- 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.)
- Active
Links
- 239000002826 coolant Substances 0.000 title 1
- 239000003507 refrigerant Substances 0.000 claims description 45
- 230000005291 magnetic effect Effects 0.000 claims description 25
- 238000004804 winding Methods 0.000 claims description 8
- 238000013459 approach Methods 0.000 claims description 5
- 239000003302 ferromagnetic material Substances 0.000 claims description 4
- 230000001846 repelling effect Effects 0.000 claims 1
- 238000007906 compression Methods 0.000 description 4
- 238000001816 cooling Methods 0.000 description 4
- 230000005284 excitation Effects 0.000 description 4
- 238000012986 modification Methods 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 230000010355 oscillation Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000000670 limiting effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000003139 buffering effect Effects 0.000 description 1
- 235000019577 caloric intake Nutrition 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000011156 evaluation Methods 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- 230000008020 evaporation Effects 0.000 description 1
- 230000005294 ferromagnetic effect Effects 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000001939 inductive effect Effects 0.000 description 1
- 239000007788 liquid Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000000717 retained effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Images
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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
- F04B17/04—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors using solenoids
-
- 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
- F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
- F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
- F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
-
- 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
- F04B49/12—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 varying the length of stroke of the working 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
- F04B2201/00—Pump parameters
- F04B2201/02—Piston parameters
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/02—Piston parameters
- F04B2201/0206—Length of piston stroke
Definitions
- the invention relates to a refrigerant compressor with a hermetically sealed compressor housing, in the interior of a refrigerant-compressing piston-cylinder unit is arranged, the cylinder housing is closed at the end by means of a cylinder head, in which a suction port and a pressure port are provided, via which refrigerant sucked via a suction valve through the suction port and is compressed via a pressure valve through the pressure port, wherein the piston-cylinder unit has at least one piston guided in a piston bore of the cylinder housing, wherein between the cylinder head and a first end face of the piston, a working space for compression a refrigerant is formed, wherein a linear drive is provided, comprising at least one vibrating body surrounded by a field winding, which is connected to the piston in order to move it oscillating along a piston longitudinal axis, according to ß the preamble of claim 1.
- the refrigeration process with azeotropic gases as such has long been known.
- the refrigerant is heated by energy intake from the space to be cooled in an evaporator and finally overheated, which leads to evaporation and compressed by a piston-cylinder unit of the refrigerant compressor to a higher pressure level, where it emits heat through a capacitor and a throttle , in which a pressure reduction and cooling of the refrigerant takes place, is transported back into the evaporator.
- Such refrigerant compressors are used in domestic and industrial applications, where they are usually arranged on the back of a refrigerator or refrigerator.
- the piston-cylinder unit comprises a cylinder housing provided with a piston bore, in which an oscillating piston is guided.
- the piston bore of the cylinder housing is closed in a first axial end of a cylinder head or a valve plate, while the piston bore is open in a second axial end portion for receiving the piston or in the assembled state of the refrigerant compressor is penetrated by a connecting rod.
- the cylinder head can generally be designed on the one hand as a solid, cap-shaped component, for example with a pressure chamber and a suction chamber, which carries a valve plate on its inside. It can be designed as an annular component which holds the valve plate on the cylinder housing, but it can also be designed only as a valve plate which is clamped by means of a clamping device on the cylindrical part of the cylinder housing.
- the suction port for sucking the refrigerant from the refrigerant circuit is arranged, and the pressure port through which the compressed refrigerant is ejected after the compression process in the refrigerant circuit through the piston.
- the valve plate is screwed to the most widespread refrigerant piston compressors with the front side of the cylinder housing.
- bores are arranged both on the cylinder housing and in the valve plate, wherein the bores in the cylinder housing are each provided with a thread, via which the screw connection is made.
- a cylinder cover having a pressure chamber in which the ejected from the cylinder, compressed Refrigerant is briefly cached, in order subsequently to flow into the refrigerant circuit.
- Embodiments are also known in which a suction chamber corresponding to the pressure chamber is provided, via which the refrigerant is sucked through the suction opening into the cylinder. Pressure chamber and suction chamber are separated from each other in such cases by appropriate structural measures in the cylinder cover.
- a refrigerant compressor of conventional design comprises an electric motor which drives the piston oscillating in the piston bore via a crankshaft.
- the disadvantage of such systems is mechanical wear in the spring elements and the piston components.
- the spring elements take up valuable space and prove to be inflexible if the cooling capacity of the refrigerant compressor or the piston stroke to be changed.
- the US 6379125 B1 also discloses a refrigerant compressor with linear drive, in which the piston is reset by means of a spring.
- Linear drives in which a piston occupies a central position due to the repulsion of Gleichpolpolter permanent magnets are in connection with vacuum pumps from US 2005/112001 A1 and the DE 10314007 A1 known.
- the DE 19504751 A1 discloses such a concept in the context of a magnetic pump for conveying liquid or gaseous media, none of which are disclosed in the last three documents mentioned However, devices meet the specific requirements of a refrigerant compressor.
- the present invention is therefore based on the object to propose a simple and reliable way to limit the piston travel in refrigerant compressors with linear drive, which makes dispensable both a providence of mechanical spring elements and a provident consuming sensor and control electronics to limit the piston travel.
- dead space should be reduced as possible.
- the piston-cylinder unit is equipped with at least one permanent magnet assembly comprising at least one arranged on the piston or on a component connected to the piston first permanent magnet and at least one arranged on the cylinder housing or on a component connected to the cylinder housing second Permanent magnet, wherein the first permanent magnet and the second permanent magnet, each having the same magnetic pole direction to each other to limit the piston travel in the region of top dead center and / or in the region of bottom dead center when approaching the first permanent magnet to the second permanent magnet a repulsive effect between the two To produce permanent magnets.
- first and second permanent magnets can be arranged in any position and constellation.
- the component connected to the piston on which the at least one first - movable - permanent magnet is arranged, it may be in a special embodiment of the invention to the oscillating body or a piston connecting the piston with the oscillating piston piston shaft.
- a valve plate may be arranged in the cylinder head, wherein the at least one second permanent magnet on the
- Valve plate preferably at least partially sunk in the valve plate, is arranged. In this way, the piston travel is limited in the region of top dead center.
- the second permanent magnet can be arranged both outside and inside or even completely or partially in the valve plate.
- the limitation of the piston travel at bottom dead center can also be done with permanent magnets, but it can also be done conventionally, for example by means of spring elements.
- the at least one second permanent magnet is disposed within the piston bore of the cylinder housing, in particular within the working space or the working space delimiting.
- one of the permanent magnets could be recessed in the cylinder housing so that it limits the working space with its front side.
- the working space is formed by the cylinder housing and designates the space swept by the piston during its oscillation within the cylinder housing.
- the at least one first permanent magnet can also be arranged outside the piston bore or the working space, for example, as already proposed above, on the oscillating body or on the piston shaft.
- a particularly simple embodiment provides that the at least one first permanent magnet is arranged in the region of the first end face of the piston facing the cylinder head.
- the at least one first permanent magnet is sunk in sections or entirely in the end face and / or in the piston skirt.
- the recessed first and / or second permanent magnet it is possible for the recessed first and / or second permanent magnet to be encased by the material of the piston or of the cylinder head or of the valve plate, preferably encased on all sides.
- the permanent magnets are sunk in the end faces of the piston and / or the valve plate, that between the permanent magnet and the piston or permanent magnet and valve plate at least one free space is present, which communicates with the working space.
- This free space preferably extends along the entire circumference of the permanent magnet.
- the gap-shaped recess favors a free development of the magnetic effect of the permanent magnet or an expansion of the magnetic field lines emanating from the permanent magnet.
- An expanding of the permanent magnet outgoing magnetic field lines is further favored by the free space is designed according to a preferred embodiment of the invention as a gap, the clear opening width widens in the direction of the working space.
- the free space can be filled with a non-ferromagnetic material, such as plastic.
- the permanent magnets can be made substantially cylindrical.
- the permanent magnets may be made substantially annular, wherein the annular shape is preferably rotationally symmetrical to the piston longitudinal axis.
- the permanent magnets in this case preferably have a ring-cylindrical shape, so that sunk permanent magnets can be surrounded by a free space in the form of an annular gap.
- the permanent magnets can also be arranged rotationally symmetrical to an axis which is parallel to the piston longitudinal axis.
- any modifications to the ring shape are also possible, e.g. oval or elliptical shapes.
- Alternative embodiments would be e.g. spiral or lattice-shaped permanent magnets.
- a plurality of permanent magnets are arranged concentrically around the piston longitudinal axis.
- the first permanent magnet arranged on the piston side essentially has a field strength of the same magnitude, that is, with the same material, preferably a substantially equal mass, on the second permanent magnet arranged on the cylinder housing side. This creates a symmetric magnetic field.
- a uniform magnetic field is also achieved when a plurality of permanent magnets are arranged on a concentric to the piston longitudinal axis circle, wherein the angular distance of adjacent permanent magnets is substantially equal.
- the piston-side and the cylinder-housing-side permanent magnets are expediently arranged on a circle, whereby the piston-side and cylinder-housing-side permanent magnets lie opposite one another (ie cover in the piston longitudinal axis).
- the piston can be designed as a double piston, comprising two at opposite End portions of the double piston arranged, one end face of the double piston forming piston sections. Between the first end face of the double piston and a first cylinder head comprising a first valve head, a first working space and between the second end face of the double piston and a second cylinder head comprising a second valve plate, a second working space is formed.
- the oscillating body is arranged between the two end faces of the double piston, preferably enclosed by the double piston, wherein an arrangement according to the invention of permanent magnets is provided for each cylinder head-piston portion pairing.
- the piston-cylinder unit is designed according to one of claims 1 to 20 and the drive strength of the linear drive is set in the case of predetermined permanent magnets in that the piston changes its direction of movement in a predetermined top dead center and / or bottom dead center without the use of a mechanical spring element.
- the piston changes its direction of movement both at the top and bottom dead center due to only one permanent magnet arrangement.
- the piston changes its direction of movement due to a permanent magnet arrangement only at one dead center, while a known spring element is used for the change of the direction of movement in the other dead center.
- the drive strength and / or frequency of the linear drive can be adjusted on the basis of measured position data of the piston or magnetic field strengths. Hall sensors such as those used in inductive encoders or current-voltage measurements of the exciter winding can be used for this purpose.
- Fig. 1 shows in a schematic way the structure of a linear compressor 23 according to the invention, which by means of a suspension device 28 within a in Figure 13 illustrated, hermetically sealed compressor housing 29 of a small refrigerant compressor is arranged.
- the linear compressor 23 comprises a piston-cylinder unit 21 with at least one piston 3 guided in a piston bore 2 of a cylinder housing 1.
- the cylinder housing 1 is closed at the end with a cylinder head 4, more precisely, with a valve plate 5 held in the cylinder head 4.
- the piston 3 is oscillatingly movable by a linear drive 6 along a piston longitudinal axis 9.
- the linear drive 6 comprises in a known manner one of a field winding (a stator) 8 surrounded oscillating body 7, which is connected to the piston 3 rigid or articulated.
- the oscillating body 7 is connected to the piston 3 by means of a piston rod or a piston stem 22.
- the piston-cylinder unit 21 is equipped with at least one permanent magnet arrangement (namely two: 11a and 12a, 11b and 12b), comprising in each case at least one component on the piston 3 or on a component connected to the piston 3 - in this case, in particular around the oscillating body 7 or around the piston skirt 22 acting-arranged first permanent magnet 11a, 11b and with at least one cylinder housing 1 or on a connected to the cylinder housing 1 component second permanent magnet 12a, 12b.
- at least one permanent magnet arrangement namely two: 11a and 12a, 11b and 12b
- the at least one first permanent magnet 11a, 11b and the at least one second permanent magnet 12a, 12b each have the same magnetic pole direction to each other, so that when approaching the at least one first permanent magnet 11 to the at least one second permanent magnet 12, a repulsive effect between the two permanent magnets 11th and 12 and thus the piston travel in the region of top dead center and / or in the region of the bottom dead center of the piston 3 limiting effect arises.
- a first permanent magnet 11a on the opposite side, a further first permanent magnet 11b is mounted, namely an annular permanent magnet.
- a second permanent magnet 12a is attached, on the opposite side of the cylinder housing 1, where the piston shaft 22 passes through the cylinder housing 1, another second permanent magnet 12b.
- the latter is ring-shaped educated.
- the permanent magnets 11a and 12a cooperate and determine the force increase in the direction of the top dead center of the piston 3, while the permanent magnets 11b and 12b cooperate and determine the increase in force in the direction of the bottom dead center of the piston 3 due to their field strength.
- the points at which the piston 3 actually reverses may vary.
- Fig. 2 is an embodiment similar to that in FIG Fig. 1 shown, only in Fig. 2 in the first end face 3 a of the piston 3, an annular permanent magnet 11 and corresponding thereto in the valve plate 5 of the cylinder head 4, an annular second permanent magnet 12 is sunk.
- the working space 14 facing surface of the first permanent magnet 11 is in a plane with the first end face 3 a of the piston 3.
- the working space 14 facing surface of the second permanent magnet 12 is in a plane with the flat inner surface of the valve plate. 5
- the valve plate 5 has a suction opening 17, which is closable on the inside of the valve plate 5 with a suction valve 15. It also has a pressure opening 18 which can be closed on the outside of the valve plate 5 with a pressure valve 16.
- the two permanent magnets 11, 12 have identical dimensions and are made of the same ferromagnetic material, so that they have the same magnetic field strength. They are designed as annular cylinder, the inner and outer surfaces thus have the shape of a cylinder jacket, the support surface on the piston 3 has the shape of a circular ring, as well as the working space 14 facing surface of the permanent magnets 11, 12th
- Both permanent magnets 11, 12 are recessed into annular recesses of the piston 3 and the valve plate 5, so that the working space 14 facing surface of the permanent magnets 11, 12 with the first end face 3a of the piston or with the inside of the valve plate 5 just finished.
- the permanent magnets 11, 12 are in each case at the bottom of the annular recess, between the cylinder surface designed as a cylindrical outer surface of the permanent magnets 11, 12 and the wall of the recess, however, a free space 13 is provided, so that the magnetic field lines - of the metallic material of the piston. 3 or the valve plate 5 undisturbed - can escape through the cylinder jacket-shaped outer surface of the permanent magnets 11, 12.
- the free space 13 may also, as shown in the piston 3, be filled with non-ferromagnetic material, such as plastic. As a result, the dead space is reduced, so that space between the piston at the dead center and valve plate, which may be filled with refrigerant.
- a further first permanent magnet such as permanent magnet 11b in Fig. 1 , are arranged with a corresponding permanent magnet 12b on the cylinder housing.
- a spring element 27 may be provided, which determines the bottom dead center of the piston 3.
- the design of the piston-cylinder unit is similar to that of Fig. 2 , Additionally is in Fig. 3 still the excitation winding 8 located.
- the first permanent magnets 11a, 11b are not arranged on the piston 3, but on the cylindrical oscillating body 7 of the linear drive 6.
- the corresponding second permanent magnets 12a, 12b are arranged on the inside of the housing 24 of the linear drive 6, so that they are aligned in the direction of the piston longitudinal axis 9 with the permanent magnets 11a, 11b.
- the permanent magnets 11a, 11b, 12a, 12b are formed here as a ring cylinder, but not recessed in the oscillating body 7 or housing 24, but attached to the circular surfaces of the oscillating body 7 and on opposite inner walls of the housing 24.
- the ring cylinders are arranged concentrically to the piston longitudinal axis 9.
- the permanent magnets 11 b and 12 b - seen in the direction of the piston longitudinal axis 9 - the lowest due to the force acting on the oscillating body 7 force of the linear drive 6 distance from each other.
- the permanent magnets 11a and 12a have the greatest possible distance from one another, which corresponds essentially to the piston stroke of the piston 3.
- Fig. 6 is detail B off Fig. 4 shown enlarged.
- the permanent magnets 11a and 12a can be seen, of the second permanent magnet arrangement (b) only permanent magnet 11b.
- the radial outer diameter of the permanent magnets 11 a and 11 b corresponds almost to the radial diameter of the cylindrical oscillating body 7, the diameter of the permanent magnets 11 a, 11 b, 12 a, 12 b is only about 1-5% smaller than that of the oscillating body 7.
- Fig. 7 shows a modification of the embodiment according to Fig. 4 in that the permanent magnet arrangement for determining the bottom dead center by Fig. 4 is replaced by a spring element 27.
- the permanent magnets 11a and 12a made Fig. 4 are retained, the permanent magnets 11 b and 12 b are replaced by the spring element 27.
- Fig. 8 shows a schematic representation of the in the region of the permanent magnets 11, 12 of the Fig. 2 and 3 developed magnetic fields in the form of field lines 25 and 26, wherein the piston 3 is in the region of its bottom dead center. Magnetic field lines are closed, they emerge at the so-called “North Pole” from the permanent magnet and at the so-called “South Pole” in this one. When a permanent magnet with its south pole approaches the north pole of another permanent magnet, the permanent magnets attract and adhere to each other.
- valve plate 5 and piston 3 are made in this embodiment of steel, so are themselves ferromagnetic, the magnetic field lines 25, 26 can therefore penetrate into the valve plate 5 and the piston 3.
- the distance between the piston 3 and piston bore 2 is shown exaggerated here.
- Fig. 9 shows the piston-cylinder assembly 21 with progressive compression stroke, the piston is on the way to top dead center.
- the magnetic fields of the two permanent magnets 11, 12 affect each other significantly more than in Fig. 8 , In the working area 14, the distance between the own field lines 25, 26 of the permanent magnet decreases, the magnetic field strength is larger, the field lines are "stretched" like a spring.
- the piston 3 has reached its top dead center. An abutment of the first end face 3 a of the piston 3 to the valve plate 5 is prevented, since the two permanent magnets 11 and 12, each with the same Magnetpolides (with the "north pole") face each other and therefore repel each other. If you were to turn off the excitation field of the excitation winding 8 now, the piston 3 would be moved by the repulsive force of the permanent magnets 11, 12 to the right.
- Fig. 11 shows a force-displacement diagram for illustrating the increase of the magnetic force when approaching the first 11 to the second permanent magnet 12.
- the magnetic force F in % On the horizontal axis, the distance between the first 11 and second permanent magnet 12 in cm, plotted on the vertical axis, the magnetic force F in %, where 100% represents the repulsive magnetic force at top dead center.
- This force must apply the linear drive 6 and the inertia of the piston 3 with the vibrating body 7 to keep the piston 3 for a short time at top dead center.
- the top dead center is given in this example at a distance of 0.05-0.5 mm between the first 11 and second permanent magnet 12. Both the diamond-shaped measuring points and the measuring curve interpolated on the basis of the measuring points are shown.
- Fig. 12 shows a piston-cylinder unit according to the invention with a double piston.
- the piston 3 is embodied as a double piston and comprises two piston sections 19, 20 arranged at opposite end regions, each forming an end face 3a, 3b of the double piston.
- a first working space is created 14 formed and between the second end face 3b of the double piston and a second valve plate 5 'comprehensive second cylinder head 4', a second working space 14 '.
- the oscillating body 7 is arranged between the two end faces 3a, 3b of the double piston, preferably enclosed by the double piston 3.
- a permanent magnet arrangement 11a, 12a or 11b, 12b according to the invention is provided for each cylinder head piston section pairing 4/19 or 4 '/ 20, a permanent magnet arrangement 11a, 12a or 11b, 12b according to the invention is provided.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Description
Die Erfindung bezieht sich auf einen Kältemittelverdichter mit einem hermetisch dichten Verdichtergehäuse, in dessen Innerem eine ein Kältemittel verdichtende Kolben-Zylinder-Einheit angeordnet ist, deren Zylindergehäuse stirnseitig mittels eines Zylinderkopfs verschlossen ist, in welchem eine Saugöffnung sowie eine Drucköffnung vorgesehenen sind, über welchen Kältemittel über ein,Saugventil durch die Saugöffnung angesaugt sowie über ein Druckventil durch die Drucköffnung verdichtet wird, wobei die Kolben-Zylinder-Einheit mindestens einen in einer Kolbenbohrung des Zylindergehäuses geführten Kolben aufweist, wobei zwischen dem Zylinderkopf und einer ersten Stirnseite des Kolbens ein Arbeitsraum zur Verdichtung eines Kältemittels ausgebildet wird, wobei ein Linearantrieb vorgesehen ist, umfassend mindestens einen von einer Erregerwicklung umgebenen Schwingkörper, welcher mit dem Kolben verbunden ist, um diesen entlang einer Kolbenlängsachse oszillierend zu bewegen, gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a refrigerant compressor with a hermetically sealed compressor housing, in the interior of a refrigerant-compressing piston-cylinder unit is arranged, the cylinder housing is closed at the end by means of a cylinder head, in which a suction port and a pressure port are provided, via which refrigerant sucked via a suction valve through the suction port and is compressed via a pressure valve through the pressure port, wherein the piston-cylinder unit has at least one piston guided in a piston bore of the cylinder housing, wherein between the cylinder head and a first end face of the piston, a working space for compression a refrigerant is formed, wherein a linear drive is provided, comprising at least one vibrating body surrounded by a field winding, which is connected to the piston in order to move it oscillating along a piston longitudinal axis, according to ß the preamble of
Der Kältemaschinenprozess mit azeotropen Gasen als solcher ist seit langem bekannt. Das Kältemittel wird dabei durch Energieaufnahme aus dem zu kühlenden Raum in einem Verdampfer erhitzt und schließlich überhitzt, was zum Verdampfen führt und mittels einer Kolben-Zylinder-Einheit des Kältemittelverdichters auf ein höheres Druckniveau verdichtet, wo es Wärme über einen Kondensator abgibt und über eine Drossel, in der eine Druckreduzierung und Abkühlung des Kältemittels erfolgt, wieder zurück in den Verdampfer befördert wird. Derartige Kältemittelverdichter finden im Haushalts- und Industriebereich Einsatz, wo sie zumeist an der Rückseite eines Kühlschranks oder Kühlregals angeordnet sind. Die Kolben-Zylinder-Einheit umfasst ein mit einer Kolbenbohrung versehenes Zylindergehäuse, in welchem ein oszillierender Kolben geführt ist.The refrigeration process with azeotropic gases as such has long been known. The refrigerant is heated by energy intake from the space to be cooled in an evaporator and finally overheated, which leads to evaporation and compressed by a piston-cylinder unit of the refrigerant compressor to a higher pressure level, where it emits heat through a capacitor and a throttle , in which a pressure reduction and cooling of the refrigerant takes place, is transported back into the evaporator. Such refrigerant compressors are used in domestic and industrial applications, where they are usually arranged on the back of a refrigerator or refrigerator. The piston-cylinder unit comprises a cylinder housing provided with a piston bore, in which an oscillating piston is guided.
Die Kolbenbohrung des Zylindergehäuses ist in einem ersten axialen Endbereich von einem Zylinderkopf bzw. von einer Ventilplatte verschlossen, während die Kolbenbohrung in einem zweiten axialen Endbereich offen für die Aufnahme des Kolbens ist bzw. im Montagezustand des Kältemittelverdichters von einem Pleuel durchsetzt ist.The piston bore of the cylinder housing is closed in a first axial end of a cylinder head or a valve plate, while the piston bore is open in a second axial end portion for receiving the piston or in the assembled state of the refrigerant compressor is penetrated by a connecting rod.
Der Zylinderkopf kann generell einerseits als massiver, kappenförmiger Bauteil, etwa mit einer Druck- und einer Saugkammer, ausgeführt sein, der an seiner Innenseite eine Ventilplatte trägt. Er kann als ringförmiger Bauteil ausgeführt sein, der die Ventilplatte am Zylindergehäuse hält, er kann aber auch nur als Ventilplatte ausgeführt sein, die mittels einer Klemmvorrichtung auf den zylindrischen Teil des Zylindergehäuses geklemmt wird. In der Ventilplatte ist dann die Saugöffnung zum Ansaugen des Kältemittels aus dem Kältemittelkreislauf angeordnet, sowie die Drucköffnung, durch welche das komprimierte Kältemittel nach dem Kompressionsvorgang in den Kältemittelkreislauf durch den Kolben ausgeschoben wird.The cylinder head can generally be designed on the one hand as a solid, cap-shaped component, for example with a pressure chamber and a suction chamber, which carries a valve plate on its inside. It can be designed as an annular component which holds the valve plate on the cylinder housing, but it can also be designed only as a valve plate which is clamped by means of a clamping device on the cylindrical part of the cylinder housing. In the valve plate then the suction port for sucking the refrigerant from the refrigerant circuit is arranged, and the pressure port through which the compressed refrigerant is ejected after the compression process in the refrigerant circuit through the piston.
Die Ventilplatte ist bei denn am weitesten verbreiteten Kältemittelkolbenkompressoren mit der Stirnseite des Zylindergehäuses verschraubt. Zu diesem Zweck sind sowohl am Zylindergehäuse als auch in der Ventilplatte Bohrungen angeordnet, wobei die Bohrungen im Zylindergehäuse jeweils mit einem Gewinde versehen sind, über welche die Verschraubung vorgenommen wird. Auf der dem Zylindergehäuse gegenüberliegenden Seite der Ventilplatte ist bei dieser am weitesten verbreiteten Art von Kältemittelkolbenkompressoren ein Zylinderdeckel vorgesehen, der eine Druckkammer aufweist, in welcher das aus dem Zylinder ausgestoßene, komprimierte Kältemittel kurz zwischengespeichert wird, um in weiterer Folge in den Kältemittelkreislauf überzuströmen. Es sind auch Ausführungsbeispiele bekannt, bei welchen eine der Druckkammer entsprechende Saugkammer vorgesehen ist, über welche das Kältemittel durch die Saugöffnung in den Zylinder gesaugt wird. Druckkammer und Saugkammer sind in solchen Fällen durch entsprechende bauliche Maßnahmen im Zylinderdeckel voneinander getrennt.The valve plate is screwed to the most widespread refrigerant piston compressors with the front side of the cylinder housing. For this purpose, bores are arranged both on the cylinder housing and in the valve plate, wherein the bores in the cylinder housing are each provided with a thread, via which the screw connection is made. On the cylinder housing opposite side of the valve plate is provided in this most common type of refrigerant piston compressors, a cylinder cover having a pressure chamber in which the ejected from the cylinder, compressed Refrigerant is briefly cached, in order subsequently to flow into the refrigerant circuit. Embodiments are also known in which a suction chamber corresponding to the pressure chamber is provided, via which the refrigerant is sucked through the suction opening into the cylinder. Pressure chamber and suction chamber are separated from each other in such cases by appropriate structural measures in the cylinder cover.
Ein Kältemittelkompressor konventioneller Bauart umfasst einen Elektromotor, welcher über eine Kurbelwelle den in der Kolbenbohrung oszillierenden Kolben antreibt.A refrigerant compressor of conventional design comprises an electric motor which drives the piston oscillating in the piston bore via a crankshaft.
Um die Vorsehung einer Kurbelwelle entbehrlich zu machen, existieren diverse Linearverdichter-Lösungen, bei welchen der Kolben direkt von einem elektrischen Linearantrieb angetrieben wird. Hierbei ist der Kolben mit einem Schwingkörper verbunden, welcher von einer Erregerwicklung (auch als Stator bezeichnet) umgebenen um entlang einer Kolbenlängsachse oszillierend in Bewegung versetzt wird. Der Kolbenhub (=Kolbenweg) kann durch eine variabel induzierte Spannung am Linearantrieb bestimmt werden.In order to make dispensable the provision of a crankshaft, there are various linear compressor solutions in which the piston is driven directly by an electric linear drive. In this case, the piston is connected to a vibrating body, which is surrounded by a field winding (also referred to as a stator) oscillating about a piston longitudinal axis is set in motion. The piston stroke (= piston travel) can be determined by a variably induced voltage at the linear drive.
Problemtisch bei solchen Lösungen ist die exakte Begrenzung des Kolbenweges während der Oszillation des Kolbens. Einerseits soll verhindert werden, dass der Kolben im Bereich des oberen Totpunkts am Zylinderkopf bzw. an der im Zylinderkopf angeordneten Ventilplatte anschlägt. Andererseits soll aber auch verhindert werden, dass sich der obere Totpunkt des Kolbens zu weit nach unten verschiebt bzw. dass der sich dem Zylinderkopf bzw. der Ventilplatte annähernde Kolben zu früh eine Umkehrbewegung vollzieht und dadurch ein leistungsvermindernder Schadraum entsteht.Problematic in such solutions is the exact limitation of the piston travel during the oscillation of the piston. On the one hand, it is intended to prevent the piston from abutting the cylinder head or the valve plate arranged in the cylinder head in the region of top dead center. On the other hand, it should also be prevented that the top dead center of the piston moves too far down or that the piston approaching the cylinder head or the valve plate takes place too early reversing movement and thereby a power-reducing dead space is created.
In den Druckschriften
Der Nachteil derartiger Systeme ist mechanischer Verschleiß in den Federelementen und den Kolbenbauteilen. Die Federelemente beanspruchen wertvollen Platz und erweisen sich als unflexibel, falls die Kälteleistung des Kältemittelkompressors bzw. der Kolbenhub verändert werden sollen.The disadvantage of such systems is mechanical wear in the spring elements and the piston components. The spring elements take up valuable space and prove to be inflexible if the cooling capacity of the refrigerant compressor or the piston stroke to be changed.
Die
Es existieren auch Linearverdichter, bei welchen der Kolben während seiner Oszillation ausschließlich durch eine elektronische Steuerung des Linearantriebs in Position gehalten wird. Solche z.B. aus der
Linearantriebe, bei welchen ein Kolben eine Mittelposition aufgrund der Abstoßung gleichgepolter Permanentmagnete einnimmt, sind im Zusammenhang mit Vakuumpumpen aus der
Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, eine einfache und zuverlässige Möglichkeit zur Begrenzung des Kolbenweges bei Kältemittelkompressoren mit Linearantrieb vorzuschlagen, welche sowohl eine Vorsehung mechanischer Federelemente als auch eine Vorsehung aufwändiger Sensor- und Steuerelektronik zur Begrenzung des Kolbenweges entbehrlich macht. Im Zylindergehäuse auftretender Schadraum soll möglichst reduziert werden.The present invention is therefore based on the object to propose a simple and reliable way to limit the piston travel in refrigerant compressors with linear drive, which makes dispensable both a providence of mechanical spring elements and a provident consuming sensor and control electronics to limit the piston travel. In the cylinder housing occurring dead space should be reduced as possible.
Erfindungsgemäß werden diese Aufgaben durch eine Vorrichtung mit den kennzeichnenden Merkmalen des Anspruchs 1 gelöst.According to the invention, these objects are achieved by a device having the characterizing features of
Dabei ist vorgesehen, dass die Kolben-Zylinder-Einheit mit mindestens einer Dauermagnetanordnung bestückt ist, umfassend jeweils mindestens einen am Kolben oder an einem mit dem Kolben verbundenen Bauteil angeordneten ersten Dauermagneten und mindestens einen am Zylindergehäuse oder an einem mit dem Zylindergehäuse verbundenen Bauteil angeordneten zweiten Dauermagneten, wobei der erste Dauermagnet und der zweite Dauermagnet mit jeweils gleicher Magnetpolrichtung zueinander weisen, um zur Begrenzung des Kolbenwegs im Bereich des oberen Totpunkts und/oder im Bereich des unteren Totpunkts bei Annäherung des ersten Dauermagneten an den zweiten Dauermagneten eine abstoßende Wirkung zwischen den beiden Dauermagneten zu erzeugen.It is provided that the piston-cylinder unit is equipped with at least one permanent magnet assembly comprising at least one arranged on the piston or on a component connected to the piston first permanent magnet and at least one arranged on the cylinder housing or on a component connected to the cylinder housing second Permanent magnet, wherein the first permanent magnet and the second permanent magnet, each having the same magnetic pole direction to each other to limit the piston travel in the region of top dead center and / or in the region of bottom dead center when approaching the first permanent magnet to the second permanent magnet a repulsive effect between the two To produce permanent magnets.
Auf diese Weise kann der Kolbenweg des Kolbens einfach und zuverlässig limitiert werden. Ein Anschlagen des Kolbens an Elementen des Zylindergehäuses, insbesondere an der Ventilplatte, wird auch ohne elektronischer Sensor- und Steuerungselemente verhindert.In this way, the piston travel of the piston can be limited easily and reliably. An abutment of the piston on elements of the cylinder housing, in particular on the valve plate is prevented even without electronic sensor and control elements.
Grundsätzlich kann eine beliebige Anzahl an ersten und zweiten Dauermagneten in beliebiger Position und Konstellation angeordnet sein.In principle, any number of first and second permanent magnets can be arranged in any position and constellation.
Bei dem mit dem Kolben verbundenen Bauteil, an welchem der mindestens eine erste - bewegliche - Dauermagnet angeordnet ist, kann es sich in einer speziellen Ausführungsvariante der Erfindung um den Schwingkörper oder um einen den Kolben mit dem Schwingkörper verbindenden Kolbenschaft handeln.In the component connected to the piston, on which the at least one first - movable - permanent magnet is arranged, it may be in a special embodiment of the invention to the oscillating body or a piston connecting the piston with the oscillating piston piston shaft.
Beim mit dem Zylindergehäuse verbundenen Bauteil, an bzw. in welchem der mindestens eine zweite - fixe - Dauermagnet angeordnet ist, handelt es sich in einer bevorzugten Ausführungsvariante der Erfindung um den Zylinderkopf.When connected to the cylinder housing component, on or in which the at least one second - fixed - permanent magnet is arranged, it is in a preferred embodiment of the invention to the cylinder head.
Dabei kann im Zylinderkopf eine Ventilplatte angeordnet sein, wobei der mindestens eine zweite Dauermagnet an derIn this case, a valve plate may be arranged in the cylinder head, wherein the at least one second permanent magnet on the
Ventilplatte, vorzugsweise zumindest abschnittsweise in der Ventilplatte versenkt, angeordnet ist. Auf diese Weise wird der Kolbenweg im Bereich des oberen Totpunkts begrenzt. Der zweite Dauermagnet kann dabei sowohl außen als auch innen an oder sogar ganz oder teilweise in der Ventilplatte angeordnet sein. Die Begrenzung des Kolbenwegs im unteren Totpunkt kann ebenfalls mit Dauermagneten erfolgen, sie kann aber auch konventionell, etwa mittels Federelementen, erfolgen.Valve plate, preferably at least partially sunk in the valve plate, is arranged. In this way, the piston travel is limited in the region of top dead center. The second permanent magnet can be arranged both outside and inside or even completely or partially in the valve plate. The limitation of the piston travel at bottom dead center can also be done with permanent magnets, but it can also be done conventionally, for example by means of spring elements.
Gemäß einer besonders bevorzugten Ausführungsvariante der Erfindung ist der mindestens eine zweite Dauermagnet innerhalb der Kolbenbohrung des Zylindergehäuses, insbesondere innerhalb des Arbeitsraumes bzw. den Arbeitsraum begrenzend angeordnet. So könnte beispielsweise einer der Dauermagnete so in das Zylindergehäuse versenkt sein, dass er mit seiner Stirnseite den Arbeitsraum begrenzt. Der Arbeitsraum wird vom Zylindergehäuse gebildet und bezeichnet den vom Kolben während seiner Oszillation durchstrichenen Raum innerhalb des Zylindergehäuses.According to a particularly preferred embodiment of the invention, the at least one second permanent magnet is disposed within the piston bore of the cylinder housing, in particular within the working space or the working space delimiting. For example, one of the permanent magnets could be recessed in the cylinder housing so that it limits the working space with its front side. The working space is formed by the cylinder housing and designates the space swept by the piston during its oscillation within the cylinder housing.
Wie bereits erwähnt, wäre es gemäß einer weiteren Ausführungsvariante der Erfindung auch möglich, den zweiten Dauermagneten außerhalb der Kolbenbohrung bzw. des Arbeitsraumes anzuordnen.As already mentioned, according to a further embodiment variant of the invention, it would also be possible to arrange the second permanent magnet outside the piston bore or the working space.
Selbstverständlich kann auch der mindestens eine erste Dauermagnet außerhalb der Kolbenbohrung bzw. des Arbeitsraumes angeordnet sein, z.B., wie bereits vorangehend vorgeschlagen, am Schwingkörper oder am Kolbenschaft.Of course, the at least one first permanent magnet can also be arranged outside the piston bore or the working space, for example, as already proposed above, on the oscillating body or on the piston shaft.
Eine besonders einfache Ausführungsform sieht vor, dass der mindestens eine erste Dauermagnet im Bereich der dem Zylinderkopf zugewandten ersten Stirnseite des Kolbens angeordnet ist.A particularly simple embodiment provides that the at least one first permanent magnet is arranged in the region of the first end face of the piston facing the cylinder head.
Um Schadraumverluste zu vermeiden, kann vorgesehen werden, dass - wie schon bei den zweiten Dauermagneten - der mindestens eine erste Dauermagnet abschnittsweise oder ganz in der Stirnseite und/oder im Kolbenschaft versenkt ist. Insbesondere ist es möglich, dass der versenkte erste und/oder zweite Dauermagnet vom Material des Kolbens oder des Zylinderkopfes bzw. der Ventilplatte ummantelt, vorzugsweise allseitig ummantelt ist.In order to avoid dead space losses, it can be provided that - as in the case of the second permanent magnets - the at least one first permanent magnet is sunk in sections or entirely in the end face and / or in the piston skirt. In particular, it is possible for the recessed first and / or second permanent magnet to be encased by the material of the piston or of the cylinder head or of the valve plate, preferably encased on all sides.
Gemäß einer Fortbildung der Erfindung ist vorgesehen, dass die Dauermagnete so in den Stirnseiten des Kolbens und/oder der Ventilplatte versenkt sind, dass zwischen Dauermagnet und Kolben bzw. Dauermagnet und Ventilplatte mindestens ein freier Raum vorhanden ist, der mit dem Arbeitsraum kommuniziert. Dieser freie Raum erstreckt sich vorzugsweise entlang des gesamten Umfangs des Dauermagneten. Die spaltförmige Ausnehmung begünstigt eine freie Entfaltung der magnetischen Wirkung des Dauermagneten bzw. ein Expandieren der vom Dauermagneten ausgehenden magnetischen Feldlinien.According to a development of the invention it is provided that the permanent magnets are sunk in the end faces of the piston and / or the valve plate, that between the permanent magnet and the piston or permanent magnet and valve plate at least one free space is present, which communicates with the working space. This free space preferably extends along the entire circumference of the permanent magnet. The gap-shaped recess favors a free development of the magnetic effect of the permanent magnet or an expansion of the magnetic field lines emanating from the permanent magnet.
Ein Expandieren der vom Dauermagneten ausgehenden magnetischen Feldlinien wird weiter begünstigt, indem der freie Raum gemäß einer bevorzugten Ausführungsvariante der Erfindung als Spalt ausgeführt ist, dessen lichte Öffnungsweite sich in Richtung des Arbeitsraumes erweitert.An expanding of the permanent magnet outgoing magnetic field lines is further favored by the free space is designed according to a preferred embodiment of the invention as a gap, the clear opening width widens in the direction of the working space.
Der freie Raum kann mit einem nicht ferromagnetischen Material, etwa Kunststoff, gefüllt sein. Durch eine solche Ausfüllung der Ausnehmung kann unerwünschter Schadraum (verbleibender Raum zwischen Kolben und Zylinderkopf bzw. Ventilplatte im oberen Totpunkt des Kolbens), welcher die Leistung des Kältemittelkompressors verringern würde, vermieden werden.The free space can be filled with a non-ferromagnetic material, such as plastic. By such a filling of the recess undesirable dead space (remaining space between the piston and cylinder head or valve plate at top dead center of the piston), which would reduce the performance of the refrigerant compressor can be avoided.
Zur optimalen Paarung der kolbenseitig angeordneten ersten und der zylindergehäuseseitig angeordneten zweiten Dauermagneten sind im Folgenden erfindungsgemäße Maßnahmen vorgeschlagen. Es soll jeweils eine fokussierte Wirkung der Dauermagnete aufeinander und eine stabile Lage des Kolbens, insbesondere während seiner Umkehrbewegung an den Totpunkten, gewährleistet sein.For optimal pairing of the piston side arranged first and the cylinder housing side arranged second permanent magnet measures according to the invention are proposed below. It should each have a focused effect of the permanent magnets each other and a stable position of the piston, in particular during its reversal movement at the dead centers, be ensured.
Die Dauermagnete können etwa im Wesentlichen zylindrisch ausgeführt sein.The permanent magnets can be made substantially cylindrical.
Insbesondere können die Dauermagnete im Wesentlichen ringförmig ausgeführt sein, wobei die Ringform vorzugsweise rotationssymmetrisch zur Kolbenlängsachse verläuft. Die Dauermagnete weisen hierbei vorzugsweise eine ringzylindrische Form auf, sodass versenkte Dauermagnete von einem freien Raum in Form eines Ringspalts umgeben sein können.In particular, the permanent magnets may be made substantially annular, wherein the annular shape is preferably rotationally symmetrical to the piston longitudinal axis. The permanent magnets in this case preferably have a ring-cylindrical shape, so that sunk permanent magnets can be surrounded by a free space in the form of an annular gap.
Die Dauermagnete können aber auch rotationssymmetrisch zu einer Achse angeordnet sein, die zur Kolbenlängsachse parallel ist.The permanent magnets can also be arranged rotationally symmetrical to an axis which is parallel to the piston longitudinal axis.
Es sind auch beliebige Modifikationen zur Ringform möglich z.B. ovale oder elliptische Formen. Alternative Ausführungsvarianten wären z.B. spiralförmige oder gitterförmige Dauermagneten. In einer speziellen Ausführungsvariante sind mehrere Dauermagnete konzentrisch um die Kolbenlängsachse angeordnet.Any modifications to the ring shape are also possible, e.g. oval or elliptical shapes. Alternative embodiments would be e.g. spiral or lattice-shaped permanent magnets. In a specific embodiment, a plurality of permanent magnets are arranged concentrically around the piston longitudinal axis.
Wenn die Stirnseite des kolbenseitig angeordneten mindestens einen ersten Dauermagneten im Wesentlichen parallel zur Stirnseite des zylindergehäuseseitig angeordneten mindestens einen zweiten Dauermagneten verläuft, ist eine gleichmäßige Ausbildung des Magnetfeldes gewährleistet.If the end face of the at least one first permanent magnet arranged on the piston side runs substantially parallel to the end face of the at least one second permanent magnet arranged on the cylinder housing side, a uniform formation of the magnetic field is ensured.
Gemäß einer weiteren bevorzugten Ausführungsvariante der Erfindung weist der kolbenseitig angeordnete erste Dauermagnet im Wesentlichen eine gleich große Feldstärke, bei gleichem Material also vorzugsweise eine im Wesentlichen gleich große Masse, auf wie der zylindergehäuseseitig angeordnete zweite Dauermagnet. Dadurch wird ein symmetrisches Magnetfeld erzeugt.According to a further preferred embodiment of the invention, the first permanent magnet arranged on the piston side essentially has a field strength of the same magnitude, that is, with the same material, preferably a substantially equal mass, on the second permanent magnet arranged on the cylinder housing side. This creates a symmetric magnetic field.
Ein gleichmäßiges Magnetfeld wird auch erreicht, wenn mehrere Dauermagnete auf einem konzentrisch zur Kolbenlängsachse verlaufenden Kreis angeordnet sind, wobei der Winkelabstand benachbarter Dauermagnete im Wesentlichen gleich groß ist. Sinnvoller Weise sind dabei jeweils die kolbenseitigen und die zylindergehäuseseitigen Dauermagnete auf einem Kreis angeordnet, wobei sich kolbenseitige und zylindergehäuseseitige Dauermagnete gegenüberliegen (also in Kolbenlängsachse gesehen decken).A uniform magnetic field is also achieved when a plurality of permanent magnets are arranged on a concentric to the piston longitudinal axis circle, wherein the angular distance of adjacent permanent magnets is substantially equal. In this case, the piston-side and the cylinder-housing-side permanent magnets are expediently arranged on a circle, whereby the piston-side and cylinder-housing-side permanent magnets lie opposite one another (ie cover in the piston longitudinal axis).
In einer speziellen Bauweise kann der Kolben als Doppelkolben ausgeführt sein, umfassend zwei an gegenüberliegenden Endbereichen des Doppelkolbens angeordnete, jeweils eine Stirnseite des Doppelkolbens ausbildende Kolbenabschnitte. Zwischen der ersten Stirnseite des Doppelkolbens und einem eine erste Ventilplatte umfassenden ersten Zylinderkopf ist ein erster Arbeitsraum und zwischen der zweitem Stirnseite des Doppelkolbens und einem eine zweite Ventilplatte umfassenden zweiten Zylinderkopf ist ein zweiter Arbeitsraum ausgebildet. Der Schwingkörper ist zwischen den beiden Stirnseiten des Doppelkolbens, vorzugsweise vom Doppelkolben eingeschlossen, angeordnet, wobei für jede Zylinderkopf-Kolbenabschnitt-Paarung eine erfindungsgemäße Anordnung von Dauermagneten vorgesehen ist.In a special construction, the piston can be designed as a double piston, comprising two at opposite End portions of the double piston arranged, one end face of the double piston forming piston sections. Between the first end face of the double piston and a first cylinder head comprising a first valve head, a first working space and between the second end face of the double piston and a second cylinder head comprising a second valve plate, a second working space is formed. The oscillating body is arranged between the two end faces of the double piston, preferably enclosed by the double piston, wherein an arrangement according to the invention of permanent magnets is provided for each cylinder head-piston portion pairing.
Bei einem erfindungsgemäßen Verfahren zur Festlegung des Kolbenweges eines Linearverdichters in einem Kältemittelkompressor gemäß dem Oberbegriff von Anspruch 1, ist vorgesehen, dass die Kolben-Zylinder-Einheit nach einem der Ansprüche 1 bis 20 ausgebildet ist und bei vorgegebenen Dauermagneten die Antriebsstärke des Linearantriebs so eingestellt wird, dass der Kolben in einem vorgegebenen oberen Totpunkt und/oder unteren Totpunkt seine Bewegungsrichtung ohne Verwendung eines mechanischen Federelements ändert.In a method according to the invention for determining the piston stroke of a linear compressor in a refrigerant compressor according to the preamble of
Es kann z.B. vorgesehen sein, dass der Kolben sowohl am oberen als auch am unteren Totpunkt seine Bewegungsrichtung nur aufgrund von jeweils einer Dauermagnetanordnung ändert. Es kann aber auch vorgesehen sein, dass der Kolben nur in einem Totpunkt seine Bewegungsrichtung aufgrund einer Dauermagnetanordnung ändert, während für die Änderung der Bewegungsrichtung im anderen Totpunkt ein bekanntes Federelement verwendet wird.It can e.g. be provided that the piston changes its direction of movement both at the top and bottom dead center due to only one permanent magnet arrangement. But it can also be provided that the piston changes its direction of movement due to a permanent magnet arrangement only at one dead center, while a known spring element is used for the change of the direction of movement in the other dead center.
Mit den Dauermagneten bildet der Kolben gemeinsam mit Schwingkörper und gegebenenfalls dem Kolbenschaft ein nichtlineares Masse-Federsystem. Dadurch sind in diesem Masse-Federsystem unterschiedliche Resonanzfrequenzen möglich, wenn man nicht den vollen Weg des Masse-Federsystems ausnützt, während in einem linearen Masse-Federsystem, wie etwa bei ausschließlicher Verwendung von Federelementen, nur eine Resonanzfrequenz auftritt, bei welcher der Kolben normalerweise betrieben wird. Erfindungsgemäß sind daher unterschiedliche Kolbenfrequenzen und damit unterschiedliche Kälteleistungen möglich.With the permanent magnets of the piston forms together with the oscillating body and possibly the piston skirt a non-linear mass-spring system. As a result, different resonance frequencies are possible in this mass-spring system, if one does not take full advantage of the mass spring system, while in a linear mass spring system, such as the exclusive use of spring elements, only one resonant frequency occurs at which the piston is normally operated. According to the invention therefore different piston frequencies and thus different cooling capacities are possible.
Entsprechend kann daher vorgesehen sein, dass - zum Erzielen unterschiedlicher Kälteleistungen - zusätzlich eine bestimmte Frequenz des Linearantriebs vorgegeben wird.Accordingly, it can therefore be provided that - to achieve different cooling capacities - in addition a certain frequency of the linear drive is specified.
Als zusätzliche Sicherheitsmaßnahme, damit der Kolben nicht an der Ventilplatte anschlägt, kann vorgesehen sein, dass Antriebsstärke und/oder Frequenz des Linearantriebs aufgrund von gemessenen Positionsdaten des Kolbens oder magnetischen Feldstärken eingestellt werden. Hierzu können etwa Hallsensoren wie in induktiven Gebern oder Strom-Spannungmessungen der Erregerwicklung Einsatz finden.As an additional safety measure, so that the piston does not hit the valve plate, it can be provided that the drive strength and / or frequency of the linear drive can be adjusted on the basis of measured position data of the piston or magnetic field strengths. Hall sensors such as those used in inductive encoders or current-voltage measurements of the exciter winding can be used for this purpose.
Die Erfindung wird nun anhand eines Ausführungsbeispiels näher erläutert. Dabei zeigt:
- Fig. 1
- eine schematische Darstellung eines erfindungsgemäßen Linearverdichters
- Fig. 2
- einen Längsschnitt durch eine erfindungsgemäßen Kolben-Zylinder-Einheit
- Fig. 3
- eine erfindungsgemäße Kolben-Zylinder-Einheit mit einem Federelement
- Fig. 4
- eine erfindungsgemäße Kolben-Zylinder-Einheit mit Dauermagneten am Schwingkörper des Linearantriebs
- Fig. 5
- die Ausführungsvariante gemäß
Fig. 4 , wobei sich der Kolben in seinem unteren Totpunkt befindet - Fig. 6
- ein Detail "B" aus
Fig. 4 - Fig. 7
- eine Modifizierung der Ausführungsvariante gemäß
Fig. 4 mit Federelement - Fig. 8
- eine schematische Darstellung der im Bereich der Dauermagnete entwickelten Magnetfelder in Form von Feldlinien (Kolben im unteren Totpunkt)
- Fig. 9
- Darstellung wie in
Fig. 8 (Kolben am Weg Richtung oberer Totpunkt) - Fig. 10
- Darstellung wie in
Fig.8 (Kolben erreicht oberen Totpunkt) - Fig. 11
- ein Kraft-Weg-Diagramm zur Darstellung des Anstiegs der Magnetkraft bei Annäherung des ersten an den zweiten Dauermagneten
- Fig. 12
- eine erfindungsgemäße Kolben-Zylinder-Einheit mit Doppelkolben
- Fig. 13
- eine schematische Darstellung eines in einem Verdichtergehäuse angeordneten erfindungsgemäßen Linearverdichters
- Fig. 1
- a schematic representation of a linear compressor according to the invention
- Fig. 2
- a longitudinal section through a piston-cylinder unit according to the invention
- Fig. 3
- an inventive piston-cylinder unit with a spring element
- Fig. 4
- an inventive piston-cylinder unit with permanent magnets on the oscillating body of the linear drive
- Fig. 5
- the embodiment according to
Fig. 4 with the piston in its bottom dead center - Fig. 6
- a detail "B" off
Fig. 4 - Fig. 7
- a modification of the embodiment according to
Fig. 4 with spring element - Fig. 8
- a schematic representation of the magnetic fields developed in the field of permanent magnets in the form of field lines (piston at bottom dead center)
- Fig. 9
- Representation as in
Fig. 8 (Piston on the way to top dead center) - Fig. 10
- Representation as in
Figure 8 (Piston reaches top dead center) - Fig. 11
- a force-displacement diagram illustrating the increase of the magnetic force upon approach of the first to the second permanent magnet
- Fig. 12
- a piston-cylinder unit according to the invention with double piston
- Fig. 13
- a schematic representation of a arranged in a compressor housing according to the invention linear compressor
Der Kolben 3 ist von einem Linearantrieb 6 entlang einer Kolbenlängsachse 9 oszillierend bewegbar. Der Linearantrieb 6 umfasst in bekannter Weise einen von einer Erregerwicklung (einem Stator) 8 umgebenen Schwingkörper 7, welcher mit dem Kolben 3 starr oder gelenkig verbunden ist. Im vorliegenden Ausführungsbeispiel ist der Schwingkörper 7 mittels einer Kolbenstange bzw. eines Kolbenschafts 22 mit dem Kolben 3 verbunden.The
Erfindungsgemäß ist die Kolben-Zylinder-Einheit 21 mit mindestens einer Dauermagnetanordnung (nämlich hier zwei: 11a und 12a; 11b und 12b) bestückt, umfassend jeweils mindestens einen am Kolben 3 oder an einem mit dem Kolben 3 verbundenen Bauteil - hierbei könnte es sich insbesondere um den Schwingkörper 7 oder um den Kolbenschaft 22 handeln-angeordneten ersten Dauermagneten 11a, 11b sowie mit mindestens einen am Zylindergehäuse 1 oder an einem mit dem Zylindergehäuse 1 verbundenen Bauteil angeordneten zweiten Dauermagneten 12a, 12b. Hierbei weisen der mindestens eine erste Dauermagnet 11a, 11b und der der mindestens eine zweite Dauermagnet 12a, 12b mit jeweils gleicher Magnetpolrichtung zueinander, sodass bei Annäherung des mindestens einen ersten Dauermagneten 11 an den mindestens einen zweiten Dauermagneten 12 eine abstoßende Wirkung zwischen den beiden Dauermagneten 11 und 12 und somit eine den Kolbenweg im Bereich des oberen Totpunkts und/oder im Bereich des unteren Totpunkts des Kolbens 3 begrenzende Wirkung entsteht.According to the invention, the piston-
Im Fall der
In
Die Ventilplatte 5 weist eine Saugöffnung 17 auf, die an der Innenseite der Ventilplatte 5 mit einem Saugventil 15 verschließbar ist. Sie weist weiters eine Drucköffnung 18 auf, die an der Außenseite der Ventilplatte 5 mit einem Druckventil 16 verschlossen werden kann.The
Beim hier dargestellten Ansaugtakt (der Kolben 3 bewegt sich nach rechts) strömt das Kältemittel über die Saugöffnung 17 am geöffneten Saugventil 15 vorbei in einen zwischen der Ventilplatte 5 und einer dieser zugewandten ersten Stirnseite 3a des Kolbens 3 ausgebildeten Arbeitsraum 14 ein. Beim Verdichtungstakt (der Kolben 3 bewegt sich dann nach links) wird Kältemittel über die Drucköffnung 18 wieder aus dem Inneren des Zylindergehäuses 1 hinausbefördert. Der Kolbenschaft 22 ist in
Die beiden Dauermagnete 11, 12 haben identische Abmessungen und sind aus dem gleichen ferromagnetischen Material gefertigt, sodass sie gleiche magnetische Feldstärke aufweisen. Sie sind als Ringzylinder ausgebildet, die inneren und die äußeren Oberflächen haben folglich die Form eines Zylindermantels, die Auflagefläche am Kolben 3 hat die Form eines Kreisrings, ebenso wie die dem Arbeitsraum 14 zugewandte Oberfläche der Dauermagnete 11, 12.The two
Beide Dauermagnete 11, 12 sind in ringförmige Vertiefungen des Kolbens 3 bzw. der Ventilplatte 5 versenkt, sodass die dem Arbeitsraum 14 zugewandte Oberfläche der Dauermagnete 11, 12 mit der ersten Stirnseite 3a des Kolbens bzw. mit der Innenseite der Ventilplatte 5 eben abschließt. Die Dauermagnete 11, 12 liegen jeweils am Boden der ringförmigen Vertiefung auf, zwischen der als Zylindermantel ausgebildeten äußeren Oberfläche der Dauermagnete 11, 12 und der Wand der Vertiefung ist jedoch ein freier Raum 13 vorgesehen, sodass die magnetischen Feldlinien - vom metallischen Material des Kolbens 3 bzw. der Ventilplatte 5 ungestört - durch die Zylindermantel-förmige äußere Oberfläche der Dauermagneten 11, 12 austreten können. Der freie Raum 13 kann auch, wie beim Kolben 3 eingezeichnet, mit nicht ferromagnetischem Material ausgefüllt sein, etwa mit Kunststoff. Dadurch wird der Schadraum verringert, also jener Raum zwischen Kolben im Totpunkt und Ventilplatte, der mit Kältemittel ausgefüllt sein kann.Both
Mit der Ausführung gemäß
Oder es kann, wie in
In der Ausführungsvariante gemäß der
Die Dauermagneten 11a, 11b, 12a, 12b sind auch hier als Ringzylinder ausgebildet, jedoch nicht im Schwingkörper 7 bzw. Gehäuse 24 versenkt, sondern an den kreisförmigen Oberflächen des Schwingkörpers 7 bzw. an gegenüber liegenden Innenwänden des Gehäuses 24 befestigt. Die Ringzylinder sind dabei konzentrisch zur Kolbenlängsachse 9 angeordnet.The
Wenn sich der Kolben 3 im oberen Totpunkt befindet, siehe
Befindet sich der Kolben 3 im unteren Totpunkt, siehe
In
Sowohl Ventilplatte 5 als auch Kolben 3 sind in diesem Ausführungsbeispiel aus Stahl gefertigt, sind also selbst ferromagnetisch, die magnetischen Feldlinien 25, 26 können daher in die Ventilplatte 5 und den Kolben 3 eindringen. Der Abstand zwischen Kolben 3 und Kolbenbohrung 2 ist hier übertrieben groß dargestellt.Both
Gemäß
Auf dieselbe prinzipielle Weise, wie der Kolbenweg gemäß den
- 11
- Zylindergehäusecylinder housing
- 22
- Kolbenbohrungpiston bore
- 33
- Kolbenpiston
- 3a3a
- erste Stirnseite des Kolbensfirst end of the piston
- 3b3b
- zweite Stirnseite des Kolbenssecond end face of the piston
- 44
- Zylinderkopfcylinder head
- 4'4 '
- zweiter Zylinderkopfsecond cylinder head
- 55
- Ventilplattevalve plate
- 5'5 '
- zweite Ventilplattesecond valve plate
- 66
- Linearantrieblinear actuator
- 77
- Schwingkörperoscillating body
- 88th
- Erregerwicklung (Stator)Excitation winding (stator)
- 99
- Kolbenlängsachsepiston longitudinal axis
- 11,11a,11b11,11a, 11b
- Erster DauermagnetFirst permanent magnet
- 12,12a,12b12,12a, 12b
- Zweiter DauermagnetSecond permanent magnet
- 1313
- Freier RaumBlank
- 1414
-
Arbeitsraum des Kolbens 3Working space of the
piston 3 - 14'14 '
-
zweiter Arbeitsraum des Kolbens 3second working space of the
piston 3 - 1515
- Saugventilsuction
- 15'15 '
- zweites Saugventilsecond suction valve
- 1616
- Druckventilpressure valve
- 16'16 '
- zweites Druckventilsecond pressure valve
- 1717
- Saugöffnungsuction opening
- 17'17 '
- zweite Saugöffnungsecond suction opening
- 1818
- Drucköffnungpressure opening
- 18'18 '
- zweite Drucköffnungsecond pressure opening
- 1919
- Erster Kolbenabschnitt des DoppelkolbensFirst piston section of the double piston
- 2020
- Zweiter Kolbenabschnitt des DoppelkolbensSecond piston section of the double piston
- 2121
- Kolben-Zylinder-EinheitPiston-cylinder unit
- 2222
- Kolbenschaftpiston shaft
- 2323
- Linearverdichterlinear compressor
- 2424
- Gehäuse des LinearantriebsHousing of the linear drive
- 2525
- Feldlinien des ersten DauermagnetsField lines of the first permanent magnet
- 2626
- Feldlinien des zweiten DauermagnetsField lines of the second permanent magnet
- 2727
- Federelementspring element
Claims (14)
- A refrigerant compressor having a hermetically sealed compressor housing, in whose interior a piston-cylinder unit (21), which compresses a refrigerant, is arranged, whose cylinder housing (1) is frontally closed by means of a cylinder head (4), in which a suction opening (17) and a pressure opening (18) are provided, via which refrigerant is suctioned in via a suction valve (15) through the suction opening and compressed via a pressure valve (16) through the pressure opening, the piston-cylinder unit (21) having at least one piston (3) guided in a piston bore (2) of the cylinder housing (1), a working space (14) for compressing a refrigerant being formed between the cylinder head (4) and a first front side (3a) of the piston (3), a linear drive (6) being provided, comprising at least one oscillating body (7) enclosed by an exciter winding (8), which is connected to the piston (3), in order to move it along a piston longitudinal axis (9) in oscillating manner, the piston-cylinder unit (21) being equipped with at least one permanent magnet arrangement, comprising respectively at least one first permanent magnet (11) arranged on the piston (3) or on a component connected to the piston (3), characterized in that the at least one permanent magnet arrangement comprises at least one second permanent magnet (12) arranged on the cylinder housing (1) or on a component connected to the cylinder housing (1), the first permanent magnet (11) and the second permanent magnet (12) pointing toward one another with the same magnetic pole direction in each case, to generate a repelling effect between the two permanent magnets (11, 12) to delimit the piston travel in the region of the top dead center and/or in the region of the bottom dead center upon approach of the first permanent magnet (11) to the second permanent magnet (12), the component connected to the cylinder housing (1), on or in which the at least one second permanent magnet (12) is arranged, is the cylinder head (4), a valve plate (5) is arranged in the cylinder head (4) and the at least one second permanent magnet (12) is arranged on the valve plate (5), preferably at least sectionally countersunk in the valve plate (5), in order to delimit the piston travel in the region of the top dead center, the permanent magnets (11, 12) are countersunk into the front side (3a, 3b) of the piston (3) and/or the valve plate (5) so that at least one free space (13) is provided between permanent magnet and piston or valve plate, which communicates with the working space (14), and this free space (13) extends along the entire periphery of the permanent magnets (11, 12).
- The refrigerant compressor according to Claim 1, characterized in that the component connected to the piston (3), on which the at least one first permanent magnet (11) is arranged, is the oscillating body (7) or a piston shaft (22) connecting the piston (3) to the oscillating body (7).
- The refrigerant compressor according to one of Claims 1 to 2, characterized in that the at least one second permanent magnet (12) is arranged inside the piston bore (2) of the cylinder housing (1).
- The refrigerant compressor according to one of Claims 1 to 3, characterized in that the at least one second permanent magnet (12) is arranged inside the working space (14) or to delimit the working space (14).
- The refrigerant compressor according to one of Claims 1 to 4, characterized in that the at least one first permanent magnet (11) is arranged in the region of the first front side (3a) of the piston (3) facing toward the cylinder head (4).
- The refrigerant compressor according to Claim 5, characterized in that the at least one first permanent magnet (11) is sectionally or entirely countersunk in the front side (3a) and/or in the piston shaft (22).
- The refrigerant compressor according to one of Claims 1 or 6, characterized in that the free space (13) is implemented as a gap, whose clear opening width widens in the direction of the working space (14).
- The refrigerant compressor according to one of Claims 6 or 7, characterized in that the free space (13) is filled using a non-ferromagnetic material.
- The refrigerant compressor according to one of Claims 1 to 8, characterized in that the at least one first permanent magnet (11) is arranged opposite to the at least one second permanent magnet (12).
- The refrigerant compressor according to one of Claims 1 to 9, characterized in that the permanent magnets (11, 12) are implemented as essentially ring-shaped, the ring shape preferably extending rotationally-symmetric to the piston longitudinal axis (9) and/or the free space preferably being implemented as a ring gap.
- The refrigerant compressor according to one of Claims 1 to 10, characterized in that one front side (11a) of the at least one first permanent magnet (11) extends substantially parallel to one front side (12a) of the at least one second permanent magnet (12).
- The refrigerant compressor according to one of Claims 6 to 11, characterized in that the at least one first permanent magnet (11) has an essentially equal field strength, preferably an essentially equal mass, as the at least one second permanent magnet (12).
- The refrigerant compressor according to one of Claims 6 to 12, characterized in that multiple permanent magnets (11, 12) are arranged on a circle extending concentrically to the piston longitudinal axis (9), the angle spacing of adjacent permanent magnets (11, 12) being essentially equal.
- The refrigerant compressor according to one of Claims 1 to 13, characterized in that the piston (3) is implemented as a double piston, comprising two piston sections (19, 20), arranged on opposing end regions of the double piston (3) and each forming one front side (3a, 3b) of the double piston, a first working space (14) being formed between the first front side (3a) of the double piston (3) and a first cylinder head (4) comprising a first valve plate (5) and a second working space (14') being formed between the second front side (3b) of the double piston (3) and a second cylinder head (4') comprising a second valve plate (5'), and the oscillating body (7) being arranged between the two front sides (3a, 3b) of the double piston (3), preferably enclosed by the double piston (3), and one permanent magnet arrangement according to one of the preceding claims being provided for each cylinder head-piston section pair (4/19, 4'/20).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT0079009U AT12038U1 (en) | 2009-12-14 | 2009-12-14 | REFRIGERANT COMPRESSOR WITH LINEAR ACTUATOR |
PCT/AT2010/000478 WO2011079330A1 (en) | 2009-12-14 | 2010-12-14 | Coolant compressor with linear drive |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2513479A1 EP2513479A1 (en) | 2012-10-24 |
EP2513479B1 true EP2513479B1 (en) | 2015-08-19 |
Family
ID=44246906
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10807312.3A Active EP2513479B1 (en) | 2009-12-14 | 2010-12-14 | Coolant compressor with linear drive |
Country Status (5)
Country | Link |
---|---|
US (1) | US20130034456A1 (en) |
EP (1) | EP2513479B1 (en) |
CN (1) | CN102741551A (en) |
AT (1) | AT12038U1 (en) |
WO (1) | WO2011079330A1 (en) |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012210347A1 (en) * | 2012-06-19 | 2013-12-19 | Hilti Aktiengesellschaft | Setting tool and control method |
US8714946B2 (en) * | 2012-09-13 | 2014-05-06 | General Electric Company | Linear compressor with an electro-magnetic spring |
DE102014205209A1 (en) * | 2014-03-20 | 2015-09-24 | Robert Bosch Gmbh | Linear drive, piston pump arrangement |
US9145878B1 (en) * | 2014-07-11 | 2015-09-29 | Marvin Ray McKenzie | Oscillating linear compressor |
US10502201B2 (en) | 2015-01-28 | 2019-12-10 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10208741B2 (en) | 2015-01-28 | 2019-02-19 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10190604B2 (en) * | 2015-10-22 | 2019-01-29 | Caterpillar Inc. | Piston and magnetic bearing for hydraulic hammer |
US10174753B2 (en) * | 2015-11-04 | 2019-01-08 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
US10830230B2 (en) | 2017-01-04 | 2020-11-10 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
CN107061221B (en) * | 2017-01-24 | 2020-03-31 | 青岛海尔智能技术研发有限公司 | Linear compressor |
US10670008B2 (en) | 2017-08-31 | 2020-06-02 | Haier Us Appliance Solutions, Inc. | Method for detecting head crashing in a linear compressor |
US10641263B2 (en) | 2017-08-31 | 2020-05-05 | Haier Us Appliance Solutions, Inc. | Method for operating a linear compressor |
CN108194312A (en) * | 2018-01-29 | 2018-06-22 | 东莞市卓奇电子科技有限公司 | Permanent magnetism oscillator piston component, asynchronous push-pull type Electromagnetic Vibrator compressor and asynchronous double-push-pull type Electromagnetic Vibrator compressibility |
CN114233719A (en) * | 2021-11-30 | 2022-03-25 | 江苏龙城鸿辉液压机电有限公司 | Buffer structure of ultra-large hydraulic hoist |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
SU1312246A2 (en) * | 1984-04-13 | 1987-05-23 | Грузинский политехнический институт им.В.И.Ленина | Electromagnetic machine |
CN2119514U (en) * | 1991-11-14 | 1992-10-21 | 臧立华 | Electricity-saving magnetic compressor |
DE19504751A1 (en) * | 1995-02-03 | 1996-08-08 | Werner Sommer | Magnet pump for liquid and gas media |
WO1998001675A1 (en) * | 1996-07-09 | 1998-01-15 | Sanyo Electric Co., Ltd. | Linear compressor |
EP1171711B1 (en) * | 1999-04-19 | 2004-10-13 | LEYBOLD VACUUM GmbH | Oscillating piston drive mechanism |
BR9907432B1 (en) | 1999-12-23 | 2014-04-22 | Brasil Compressores Sa | COMPRESSOR CONTROL METHOD, PISTON POSITION MONITORING SYSTEM AND COMPRESSOR |
DE10314007A1 (en) * | 2003-03-28 | 2004-10-07 | Leybold Vakuum Gmbh | Piston vacuum pump for pumping gas, has sensor that detects speed of switching supply of energizing current between electrical coils by magnet arrangement |
DE102006009256A1 (en) | 2006-02-28 | 2007-08-30 | BSH Bosch und Siemens Hausgeräte GmbH | Compressor apparatus for household cooling equipment e.g. refrigerator, freezer has linear drive having adjustable rotor zero position, and linear compressor having adjustable piston zero position |
DE102006009270A1 (en) | 2006-02-28 | 2007-08-30 | BSH Bosch und Siemens Hausgeräte GmbH | Linear compressor for cooling equipment e.g. refrigerator, freezer has linkage having spring, and which couples compressor piston to drive |
BRPI0800251B1 (en) | 2008-02-22 | 2021-02-23 | Embraco Indústria De Compressores E Soluções Em Refrigeração Ltda | linear compressor control system and method |
CN101240793B (en) | 2008-03-14 | 2011-04-27 | 刘新春 | Linear motor double cylinder compression pump |
-
2009
- 2009-12-14 AT AT0079009U patent/AT12038U1/en not_active IP Right Cessation
-
2010
- 2010-12-14 US US13/515,583 patent/US20130034456A1/en not_active Abandoned
- 2010-12-14 CN CN2010800626814A patent/CN102741551A/en active Pending
- 2010-12-14 WO PCT/AT2010/000478 patent/WO2011079330A1/en active Application Filing
- 2010-12-14 EP EP10807312.3A patent/EP2513479B1/en active Active
Also Published As
Publication number | Publication date |
---|---|
US20130034456A1 (en) | 2013-02-07 |
EP2513479A1 (en) | 2012-10-24 |
CN102741551A (en) | 2012-10-17 |
WO2011079330A1 (en) | 2011-07-07 |
AT12038U1 (en) | 2011-09-15 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2513479B1 (en) | Coolant compressor with linear drive | |
DE4015006C2 (en) | ||
DE10203703B4 (en) | Piston compressor with electromagnetic linear motor | |
WO2009013131A1 (en) | Stroke-regulated linear compressor | |
EP1171711A1 (en) | Rotary piston drive mechanism | |
EP2284341B1 (en) | Fastener for locking an opening | |
EP0506799A1 (en) | Magnetic drive with permanent-magnet solenoid armature. | |
DE102005000894A1 (en) | Reciprocating compressor for use in refrigerator, has motor with inner stator that is arranged at inner circumferential surface of outer stator, where winding coil is wound around inner stator | |
WO2007098995A1 (en) | Linear drive and linear compressor with adaptable output | |
EP0977017A1 (en) | Wear monitor | |
EP2304234B1 (en) | Linear compressor | |
DE4342318C2 (en) | Swash plate compressor | |
DE3109455C2 (en) | Swing compressor | |
DE4122340C2 (en) | Swashplate refrigerant compressor with variable output | |
WO2018178117A1 (en) | Piston compressor valve and method for operating a piston compressor valve | |
WO2009013105A1 (en) | Linear compressor | |
DE10331916A1 (en) | Drive device for generating a reciprocating movement of a driven component, in particular in weaving machines | |
DE10019108A1 (en) | Oscillating piston drive | |
DE102006059762A1 (en) | piston compressor | |
DE102005038785B4 (en) | Linear compressor, in particular refrigerant compressor | |
EP3601798B1 (en) | Valve closure for a piston compressor valve and method of operating the valve closure | |
DE102010003772A1 (en) | linear compressor | |
EP2137407B1 (en) | Piston engine, especially for dental and medical purposes | |
DE3719460A1 (en) | Method for driving a pump's pumping element connected to an oscillating-armature drive, and pump working according to it | |
EP3488107A1 (en) | Oscillating displacement pump having an electrodynamic drive and method for operation thereof |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20120626 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
DAX | Request for extension of the european patent (deleted) | ||
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SECOP AUSTRIA GMBH |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: SECOP AUSTRIA GMBH |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20150310 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 744028 Country of ref document: AT Kind code of ref document: T Effective date: 20150915 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502010010121 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151120 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151119 |
|
REG | Reference to a national code |
Ref country code: SK Ref legal event code: T3 Ref document number: E 19511 Country of ref document: SK |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151221 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151219 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502010010121 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151231 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20160520 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20151214 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20151214 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R082 Ref document number: 502010010121 Country of ref document: DE Representative=s name: KUHNEN & WACKER PATENT- UND RECHTSANWALTSBUERO, DE Ref country code: DE Ref legal event code: R081 Ref document number: 502010010121 Country of ref document: DE Owner name: SECOP GMBH, DE Free format text: FORMER OWNER: SECOP AUSTRIA GMBH, FUERSTENFELD, AT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20160831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151214 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151231 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151231 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151214 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151231 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 744028 Country of ref document: AT Kind code of ref document: T Effective date: 20151214 |
|
REG | Reference to a national code |
Ref country code: SK Ref legal event code: PC4A Ref document number: E 19511 Country of ref document: SK Owner name: SECOP GMBH, FLENSBURG, DE Free format text: FORMER OWNER: SECOP AUSTRIA GMBH, FUERSTENFELD, AT Effective date: 20170315 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20101214 Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20151214 Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150819 |
|
P01 | Opt-out of the competence of the unified patent court (upc) registered |
Effective date: 20230517 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SK Payment date: 20231129 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20231221 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20231227 Year of fee payment: 14 |