CN102741551A

CN102741551A - Coolant compressor with linear drive

Info

Publication number: CN102741551A
Application number: CN2010800626814A
Authority: CN
Inventors: H·P·舍格勒
Original assignee: ACC Austria GmbH
Current assignee: Saikepu Austria GmbH
Priority date: 2009-12-14
Filing date: 2010-12-14
Publication date: 2012-10-17
Also published as: US20130034456A1; EP2513479A1; AT12038U1; EP2513479B1; WO2011079330A1

Abstract

The invention relates to a coolant compressor with a hermetically sealed compressor housing, in the interior of which lies a piston cylinder unit (21) that compresses a coolant. The cylinder housing (1) of said piston cylinder unit is closed at the front end thereof by means of a cylinder head (4), said piston cylinder unit (21) having at least one piston (3). A linear drive (6) is provided, comprising at least one oscillating body (7) which is surrounded by an excitation winding (8) and which is connected to the piston (3) in order to move same along a longitudinal axis (9) of the piston in an oscillating manner. According to the invention, the piston cylinder unit (21) is equipped with at least one permanent magnet arrangement, each permanent magnet arrangement comprising at least one first permanent magnet (11) that lies on the piston (3) and at least one second permanent magnet (12) that lies on the cylinder housing (1). Both the first permanent magnet (11) and the second permanent magnet (12) face each other and are oriented in the same magnetic pole direction in order to generate a repelling effect between both permanent magnets (11, 12) to limit the path of the piston in the region of the top dead center and/or in the region of the bottom dead center.

Description

Coolant compressor with Linear actuator

Technical field

The present invention relates to a kind of coolant compressor with closed compressor shell as described in the preamble according to claim 1; The piston cylinder units of compressed refrigerant is disposed in the inside of this compressor case; The cylinder baffle of piston cylinder units is sealed by cylinder head at end face; In this cylinder head, be provided with suction opening and pressure opening, via this suction opening and pressure opening, refrigeration agent is sucked by suction opening via suction valve and is compressed by the pressure opening via pressure valve; Wherein piston cylinder units has at least one piston that in the piston hole of cylinder baffle, guides; The working space that wherein is used for compressed refrigerant is formed between first end face of cylinder head and piston, wherein is provided with Linear actuator, and this Linear actuator comprises at least one oscillating body that is surrounded by field coil; This oscillating body is connected to piston, so that piston is moved with vibration mode along the direction of piston longitudinal axis.

Background technique

Use the Coolers technology of azeotropic gas itself for some time known.Be heated through the energy that absorbs the space to be cooled in the from evaporator drier and overheated at last at this refrigeration agent; This causes evaporating and the piston cylinder units through coolant compressor is compressed to higher stress level, and refrigeration agent is carried back in the vaporizer via the condenser released heat and via throttle valve (in this throttle valve, realize pressure descends and the cooling of refrigeration agent) at this once more.This coolant compressor uses at civilian and industrial field, and wherein this coolant compressor typically is disposed in the dorsal part of refrigerator or refrigerated shelf.

Piston cylinder units comprises the cylinder baffle that is provided with piston hole, in this cylinder baffle, guides vibration type piston.

The piston hole of cylinder baffle in first axial end region by cylinder head or by valve plate sealing, and piston hole second axial end region be open wide to hold piston, perhaps under the installment state of coolant compressor, passed by connecting rod.

Cylinder head can be configured to the parts of the lid shape of entity usually on the one hand, for example has pressure chamber and suction chamber, and these parts side within it carry valve plate.These parts can be configured to ring-shaped member, and it remains on valve plate on the cylinder baffle, yet it can also only be configured to valve plate, and this valve plate is clamped on the cylindrical part of cylinder baffle through chucking device.In this case, be used for the suction opening of refrigeration agent sucking-off refrigerant circuit is disposed in valve plate, the pressure opening also is disposed in the valve plate, and refrigerant compressed is discharged by piston through the pressure opening after the refrigerant circuit compression process.

In the most general refrigeration agent piston compressor, valve plate is connected with the end-face helical of cylinder baffle.For this reason, on the cylinder baffle and hole arranged in valve plate, wherein the hole in cylinder baffle is equipped with screw thread, carries out being threaded through this screw thread.In the coolant compressor of this general types; Valve plate with the opposed side of cylinder baffle on be provided with cylinder cover; This cylinder cover has pressure chamber, the refrigerant compressed of discharging from cylinder this pressure chamber by temporary cache, so that overflow in the refrigerant circuit subsequently.Also known such embodiment wherein is provided with the suction chamber corresponding to pressure chamber, and via this suction chamber, refrigeration agent is drawn in the cylinder by suction opening.Pressure chamber and suction chamber are separated from one another through the structural measure of the correspondence in the cylinder in this case.

The coolant compressor of conventional construction comprises motor, the piston that this motor vibrates in piston hole via crank-driven.

For bent axle is provided redundantly, there are various Linearkompressor schemes, wherein piston is directly driven by electromotion linearity driver.In the case, piston is connected to oscillating body, and the oscillating body that is surrounded by exciting winding (also being called as stator) is configured to move with vibration mode along the longitudinal axis of piston.Stroke of piston (=piston stroke) can be confirmed by the variable induced voltage on the Linear actuator.

In this solution, the accurate restriction of the piston stroke during piston vibration is problematic.Should prevent on the one hand that in the zone of upper dead center piston is on the cylinder head or be arranged on the valve plate in the cylinder head and impact.Yet on the other hand, should prevent that also the upper dead center displacement downwards of piston is too far away, perhaps prevent to carry out reversing motion too early and thereby the clearance space of decreased performance occurs near the piston of cylinder head or valve plate.

For this reason, the mechanical spring element that in document CN 101240793A and DE 10 2,006 009 270A, proposes to be used for damper piston and therefore be used for the limited piston stroke.Known according to DE 102,006 009 256A, change piston stroke through adjustable spring element.

The shortcoming of this system is the mechanical wear in spring element and the piston element.Spring element occupies expensive real estate, and confirms: change the refrigerating capacity or the stroke of piston of coolant compressor if desired, then spring element is inflexible.

Also have such Linearkompressor, wherein piston only is held in place by the electronic controller of Linear actuator during its vibration.Yet this solution (it is known according to WO 01/48379A and WO 2009/103138 A2 for example) that is used for the limited piston stroke only just can be implemented under the situation that complex sensing technology and analytical technology are provided.The sensor of the endurance of confirming piston motion particularly is provided, this endurance subsequently by microprocessor be stored in comparing with reference to the endurance on the storage medium, and calculate the current location of piston thus.Therefore this system expensive is seldom used in compressor is in batches made.

Summary of the invention

Therefore; The purpose that the present invention is based on provides a kind of simple and reliable possible scheme; Be used for having the coolant compressor limited piston stroke of Linear actuator; It not only provides the mechanical spring element, and redundant the complex sensing electronic device and control electronic device that is provided for the limited piston stroke.The clearance space that in cylinder baffle, occurs is also reduced as much as possible.

According to the present invention, the equipment of characteristic each characteristic of these purposes through having claim 1 is achieved.

At this a kind of piston cylinder units is provided; It is equipped with at least one permanent magnet layout; This at least one permanent magnet layout comprises respectively and is arranged on the piston or is arranged at least one first permanent magnet on the parts that are connected to piston and is arranged on the cylinder baffle or is arranged at least one second permanent magnet on the parts that are connected to cylinder baffle; Wherein first permanent magnet points to each other with identical pole orientation respectively with second permanent magnet; So that between two permanent magnets, produce repulsive interaction, thereby at first permanent magnet limited piston stroke in the zone at upper dead center and/or in the zone at lower dead centre during near second permanent magnet.

The piston stroke of piston can limit in this way simple and reliablely.Also prevent on the element of piston slap at cylinder baffle under the situation that does not have electronic sensor and control unit, particularly on the valve plate.

In principle, during first and second permanent magnets of any amount can be disposed in the arbitrary position and construct.

In specific embodiment modification of the present invention, the said parts that are furnished with movably said at least one first permanent magnet that are connected to piston can be for oscillating body or for piston being connected to the piston shaft of oscillating body.

In the preferred embodiments of the present invention modification, the said parts that are connected to fixing said at least one second permanent magnet of being furnished with of piston shell are cylinder head.

In cylinder head, can arrange valve plate at this, wherein said at least one second permanent magnet is disposed on this valve plate, and preferably dress is embedded in this valve plate at least in part.In this way, limited piston stroke in the zone of upper dead center.Can be externally and be disposed on the valve plate in inside or even completely or partially be arranged in the valve plate at this second permanent magnet.Also can use permanent magnet to realize at lower dead centre limited piston stroke, however its can also be according to tradition, for example realize by means of spring element.

According to the modification of alternate embodiments of the present invention, the said parts that are connected to said at least one second permanent magnet of being furnished with of cylinder baffle are for surrounding the shell of oscillating body.This shell is preferably the holding device that is used for exciting winding (stator) or is exciting winding itself.

According to the modification of special preferred embodiment of the present invention, said at least one second permanent magnet is disposed in the inside of the piston hole of cylinder baffle, particularly is arranged in the inside or the restraint of labour space of working space.Thereby for example, one of permanent magnet can be embedded in the cylinder baffle by dress, thus the end face restraint of labour space of this permanent magnet.Working space is formed by cylinder baffle, and in cylinder baffle, limits the space of piston process during its vibration.

As stated, modification according to a further embodiment of the invention can also be arranged in second permanent magnet outside of piston hole or working space.

Certainly, said at least one first permanent magnet also can be disposed in the outside of piston hole or working space, for example is arranged on the oscillating body as stated or is arranged on the piston shaft.

For limited piston stroke in the zone of upper dead center alternately or additionally, can be provided with other or another permanent magnet layout, wherein said at least one second permanent magnet be disposed in cylinder baffle with the opposed end regions of cylinder head in.Suitablely at this be, said at least one first permanent magnet be disposed in piston away from second end face of cylinder head or on piston shaft.

Special simple embodiment regulation, said at least one first permanent magnet be disposed in piston in the zone of first end face of cylinder head.

For fear of the clearance space loss, can stipulate that as the situation of second permanent magnet, said at least one first permanent magnet is partially or even wholly adorned to be embedded in the end face and/or to adorn and is embedded in the piston shaft.Especially, possible is that first and/or second permanent magnet that dress buries is covered by the material of piston or cylinder head or valve plate, preferably all is capped in all sides.

According to improvement of the present invention regulation: permanent magnet is embedded in the piston end face by dress and/or in the valve plate, thereby between permanent magnet and piston or between permanent magnet and valve plate, has at least one free space that is communicated with working space.This free space preferably extends along the whole circumference of permanent magnet.The groove of gap-like promotes the expansion that freely launches or derive from the magnetic field line of permanent magnet of the magnetic effect of permanent magnet.

According to a preferred embodiment of the invention, through free space is configured to the gap, the clear opening width in this gap broadens towards the direction of working space, and further promotion derives from the expansion of the magnetic field line of permanent magnet.

Free space can use nonferromagnetic material, for example plastics to fill.Through this filling of groove, can avoid undesirable clearance space (at the remaining space of upper dead center between piston and cylinder head or valve plate of piston), undesirable clearance space can reduce the performance of coolant compressor.

Modification according to another preferred embodiment of the invention, first permanent magnet of arranging in piston side is arranged to mutually opposed with second permanent magnet of arranging in the cylinder baffle side.Two permanent magnets for example can be arranged in the piston longitudinal axis identically.

For best pairing is arranged in first permanent magnet on the piston side and is arranged in second permanent magnet on the cylinder baffle side, measure is proposed below according to the present invention.In all cases, particularly during the reversing motion of piston, guarantee that permanent magnet is to each other the focussing force and the settling position of piston at dead point place.

Permanent magnet can for example be configured to substantially cylindrical.

Particularly, permanent magnet can be configured to annular basically, and this annular is preferably about piston longitudinal axis rotation extension symmetrically.Permanent magnet preferably has the ring cylinder form in the case, thereby the permanent magnet that dress buries can be surrounded by the free space of annular space form.

But permanent magnet can also be arranged to about being parallel to the axis rotation symmetry of piston longitudinal axis.

Any variant of annular shape also is fine, and is for example avette or oval.The modification of alternate embodiments can for example be helical or grid-like permanent magnet.In the certain embodiments modification, a plurality of permanent magnets are arranged around the piston longitudinal axis with one heart.

If be arranged in the end face extension that the end face of at least one first permanent magnet on the piston side is basically parallel at least one second permanent magnet that is arranged on the cylinder baffle side, then guarantee to be formed uniformly magnetic field.

According to the modification of further preferred embodiment of the present invention, first permanent magnet that is arranged on the piston side has the field intensity that equates basically with second permanent magnet on being arranged in the cylinder baffle side, therefore under the situation of equivalent material, has the basic quality that equates.Thereby the magnetic field that produces symmetry.

If a plurality of permanent magnets are disposed on the circle that extends with one heart about the piston longitudinal axis, the angular separation of wherein adjacent permanent magnet is equal basically, also realizes uniform magnetic field.Advantageously be arranged on the circle at the permanent magnet of this piston side and the permanent magnet of cylinder shell side, wherein the permanent magnet of piston side mutually opposed with the permanent magnet of cylinder shell side (that is, superimposed to watching) along the piston longitudinal shaft.

In the structure of particular type, piston can be configured to double-piston, comprises two piston sections, and these two piston sections are disposed on the opposed end regions of double-piston and an end face of each self-forming double-piston.At first end face of double-piston and comprise between first cylinder head of first valve plate and form first working space, formation second working space between second end face of double-piston and second cylinder head that comprises second valve plate.Oscillating body is disposed between two end faces of double-piston, is preferably surrounded by double-piston, wherein is directed against each cylinder head-piston section to being provided with one according to permanent magnet layout of the present invention.

Stipulating in the method for the piston stroke of confirming Linearkompressor according to the coolant compressor as described in the preamble of claim 1 according to of the present invention being used for: piston cylinder units is according to each structure in the claim 1 to 20; And under the situation of given in advance permanent magnet; Set the drive strength of Linear actuator like this; Make piston in given in advance upper dead center and/or lower dead centre, change the moving direction of this piston, and do not use the spring element of machinery.

For example can stipulate that piston all only changes its moving direction based on a corresponding permanent magnet layout at upper dead center and lower dead centre.Yet, can also stipulate that piston only changes its moving direction based on a permanent magnet layout in a dead point, and in order in another dead point, to change moving direction, uses known spring element.

Adopt permanent magnet, piston and oscillating body also form nonlinear mass-spring system with piston shaft alternatively jointly.Therefore, if do not utilize the total travel of mass-spring system, then resonant frequency maybe be different in this mass-spring system; And in the linear quality spring system; Under the situation of only using spring element, a resonant frequency only appears for example, piston under this resonant frequency by normal running.Therefore, according to the present invention, can realize different piston frequency and so different refrigerating capacity.

Therefore correspondingly, can stipulate, in order to realize different refrigerating capacities, the frequency of confirming of given Linear actuator in advance also.

As extra safety measure,, can stipulate that the drive strength of Linear actuator and/or frequency are set based on the position of piston data or the magnetic intensity that measure for piston does not impinge upon on the valve plate.For this reason, as in the current-voltage measurement of inductive encoder or exciting winding, for example can use Hall transducer.

Description of drawings

Explain the present invention in more detail based on embodiment now.In the accompanying drawings:

Fig. 1 shows the schematic representation according to Linearkompressor of the present invention.

Fig. 2 shows through the longitudinal cross-section according to piston cylinder units of the present invention.

Fig. 3 shows according to the piston cylinder units with spring element of the present invention.

Fig. 4 shows according to the piston cylinder units with the permanent magnet on the oscillating body that is positioned at Linear actuator of the present invention.

Fig. 5 shows the embodiment variant according to Fig. 4, and wherein piston is positioned at its lower dead centre.

The thin portion " B " of Fig. 6 displayed map 4.

Fig. 7 shows the variation according to the embodiment variant with spring element of Fig. 4.

Fig. 8 is presented at the schematic representation (piston is at lower dead centre) in the magnetic field of developing in the zone of permanent magnet with the form of field wire.

Fig. 9 shows like the view among Fig. 8 (piston is on the stroke of the direction of upper dead center).

Figure 10 shows like the view among Fig. 8 (piston arrives upper dead center).

Figure 11 shows power-stroke chart, the increase of magnetic force when being illustrated in first permanent magnet near second permanent magnet.

Figure 12 shows according to the piston cylinder units with double-piston of the present invention.

Figure 13 shows the schematic representation of the Linearkompressor of arrangement according to the invention in compressor case.

Embodiment

Fig. 1 schematically shows the structure according to Linearkompressor 23 of the present invention, and this Linearkompressor 23 is arranged in the inside of the closed compressor shell 29 (shown in Figure 13) of small refrigerant compressor through suspension equipment 28.Linearkompressor 23 comprises piston cylinder units 21, and this piston cylinder units has at least one piston 3 of guiding in the piston hole 2 of cylinder baffle 1.Cylinder baffle 1 utilizes cylinder head 4 sealings at end face, more specifically utilizes valve plate 5 sealings that remain in the cylinder head 4.

Piston 3 can move with vibration mode along piston longitudinal axis 9 through Linear actuator 6.In known way, Linear actuator 6 comprises the oscillating body 7 that is surrounded by exciting winding (stator) 8, and this oscillating body is with piston 3 rigidity or hingedly be connected.In the present embodiment, oscillating body 7 is connected to piston 3 through piston rod or piston shaft 22.

According to the present invention, it (is two at this promptly: 11a and 12a that piston cylinder units 21 is equipped with at least one permanent magnet layout; 11b and 12b); Comprise respectively: be arranged on the piston 3 or be arranged at least one first permanent magnet 11a, the 11b on the parts (can be oscillating body 7 or piston shaft 22 at these these parts especially) that are connected to piston 3, and be arranged on the cylinder baffle 1 or be arranged at least one second permanent magnet 12a, the 12b on the parts that are connected to cylinder baffle 1.At this; At least one first

permanent magnet

11a, 11b and at least one second

permanent magnet

12a, 12b point to each other with identical pole orientation respectively; Thereby when at least one first permanent magnet 11 during near at least one second permanent magnet 12; Therefore between two

permanent magnets

11 and 12, produce repulsive interaction, be created in the effect of limited piston stroke in the zone of zone and/or lower dead centre of upper dead center of piston 3.

Under the situation of Fig. 1, one first permanent magnet 11a is attached to the end face of piston 3, another first permanent magnet 11b, is that the annular permanent-magnet body is attached to opposite side.One second permanent magnet 12a is attached to cylinder head 4 or is attached to the valve plate of cylinder head 4, and another second permanent magnet 12b is attached to the opposite side of cylinder baffle 1, passes cylinder baffle 1 at this opposite side place piston shaft 22.Another second permanent magnet is configured to ring-type.Confirm to increase in this

permanent magnet

11a and 12a cooperation and based on their field intensity, and permanent magnet 11b confirms towards the power increase of the lower dead centre direction of piston 3 with the 12b cooperation and based on their field intensity towards the power of the upper dead center direction of piston 3.According to load, the point during piston 3 actual steerings can change.

Fig. 2 demonstration is similar to embodiment embodiment illustrated in fig. 1, and just in Fig. 2, annular permanent-magnet body 11 dresses are embedded among the first end face 3a of piston 3, and ring-type second permanent magnet 12 is adorned in the valve plate 5 that is embedded in cylinder head 4 with annular permanent-magnet body 11 accordingly.First permanent magnet 11 towards the first end face 3a of the surface of working space 14 and piston 3 in a plane.Second permanent magnet 12 towards the flat inner surface of the surface of working space 14 and valve plate 5 in a plane.

Valve plate 5 has suction opening 17, and this suction opening 17 can utilize suction valve 15 sealings in the inboard of valve plate 5.Valve plate 5 also has pressure opening 18, and this pressure opening can utilize pressure valve 16 sealings in the outside of valve plate 5.

During aspirating stroke shown here (piston 3 moves right), refrigeration agent flow in the operation interval 14 through the suction valve of opening 15 via suction opening 17, this operation interval be formed on valve plate 5 and piston 3 towards between the first end face 3a of valve plate 5.During compression stroke (piston 3 is moved to the left), refrigeration agent leaves the inside output of cylinder baffle 1 once more via pressure opening 18.Piston shaft 22 does not show in Fig. 2.

Two

permanent magnets

11,12 have same size and by identical ferromagnetic material manufacturing, thereby these two permanent magnets have equal magnetic intensity.These two permanent magnets are configured to circular cylinder, so internal surface and outer surface have the form of cylindrical sheath, and the supporting surface on the piston 3 has the form of circular ring, the form that has circular ring towards the surface of operation interval 14 equally of

permanent magnet

11,12.

Two

permanent magnets

11,12 are embedded in the annular recess of piston 3 or valve plate 5 by dress respectively, thus evenly the stopping of

permanent magnet

11,12 towards the first end face 3a of the surface of working space 14 and piston or with the inboard of valve plate 5.

Permanent magnet

11,12 is placed in the bottom of annular recess separately; Yet between the wall of the outer surface that is configured to cylindrical sheath of

permanent magnet

11,12 and depression, be provided with free space 13, thereby not left by the outer surface of the cylindrical sheath form that magnetic field line that the metallic material of piston 3 or valve plate 5 disturbs can be through permanent magnet 11,12.As shown in the piston 3, free space 13 can also use nonferromagnetic material to fill, and for example uses plastics to fill.Reduce clearance space thus, i.e. the space of the enough refrigeration agent fillings of the ability between piston that is in the dead point and valve plate.

Use is according to the embodiment of Fig. 2, and piston stroke is limited by

permanent magnet

11,12 at upper dead center.For the limited piston stroke at the lower dead centre place, another first permanent magnet (like the permanent magnet 11b among Fig. 1) also can be disposed on the second end face 3b of piston 3, and corresponding permanent magnet 12b is arranged on the cylinder baffle.

Perhaps, as shown in Figure 3, spring element 27 can be provided, this spring element is confirmed the lower dead centre of piston 3.The structure of piston cylinder units is identical with structure among Fig. 2.In addition, exciting winding 8 is also shown among Fig. 3.

In the embodiment variant according to Fig. 4-6, the first

permanent magnet

11a, 11b are not arranged on the piston 3, but are arranged on the cylindrical oscillating body 7 of Linear actuator 6.The corresponding second

permanent magnet

12a, 12b are disposed on the inboard of shell 24 of Linear actuator 6, thereby corresponding second permanent magnet aligns with

permanent magnet

11a, 11b along the direction of piston longitudinal axis 9.

Permanent magnet

11a, 11b, 12a, 12b also are configured to circular cylinder at this, but are not embedded in shell 24 or the oscillating body 7 by dress, but are fastened on the circular surface of oscillating body 7 or are fastened on the opposed inwall of shell 24.Each circular cylinder is arranged about piston longitudinal axis 9 at this with one heart.

When piston 3 is positioned at upper dead center, referring to Fig. 4, watch along the direction of piston longitudinal axis 9,

permanent magnet

11a and 12a have minimum possible spacing relative to each other because of the power that acts on the oscillating body 7 of Linear actuator 6.Yet

permanent magnet

11b and 12b have the spacing relative to each other of maximum possible, and the spacing of this maximum possible corresponds essentially to the stroke of piston of piston 3.

If piston 3 is positioned at lower dead centre, referring to Fig. 5, watch along the direction of piston longitudinal axis 9,

permanent magnet

11b and 12b have minimum possible spacing relative to each other because of the power that acts on the oscillating body 7 of Linear actuator 6.Yet

permanent magnet

11a and 12a have the spacing relative to each other of maximum possible, and the spacing of this maximum possible corresponds essentially to the stroke of piston of piston 3.

Fig. 6 is to amplify the thin B of portion of form displayed map 4.

Permanent magnet

11a and 12a are visible in a permanent magnet layout (a), and it is visible in the second permanent magnet layout (b), having only permanent magnet 11b.The radial outer diameter of

permanent magnet

11a and 11b is almost corresponding to the radial diameter of cylindrical oscillating body 7, and the diameter of

permanent magnet

11a, 11b, 12a, 12b is only than the little about 1-5% of diameter of oscillating body 7.

Fig. 7 shows the variant according to the embodiment variant of Fig. 4, and the permanent magnet layout that wherein is used for the lower dead centre of definite Fig. 4 is substituted by spring element 27.Permanent magnet 11a and the 12a of Fig. 4 are held, and

permanent magnet

11b and 12b are substituted by spring element 27.

Fig. 8 is presented at the schematic representation in the magnetic field of developing in the zone of the permanent magnet 11,12 among Fig. 2 and Fig. 3 with the form of field wire 25 or 26, and wherein piston 3 is arranged in the zone of its lower dead centre at this.Magnetic field line is closed, and it leaves permanent magnet in so-called " arctic " respectively, and gets into permanent magnet in so-called " South Pole ".When South Pole of a permanent magnet during near arctic of another permanent magnet, permanent magnet attracts each other and absorption each other.If the arctic of a permanent magnet is during near arctic (perhaps the South Pole of a permanent magnet is near the South Pole of another permanent magnet) of another permanent magnet; Two permanent magnet repulsions, permanent magnet can not close to each other or only possibly utilize certain power close to each other and make the contact of its South Pole.This principle obtains utilizing in the present invention.Because the repulsive force between the magnetic pole of the same name and the spacing of magnetic pole are inversely proportional to, so piston 3 also is non-linear near the power of valve plate 5 and the spacing between piston 3 and the valve plate 5.This is and is arranged in the essential distinction of the spring element between valve plate 5 and the piston 3, wherein the spacing linear correlation between power and valve plate 5 and the piston 3.

Valve plate 5 and piston 3 are all made by steel in this exemplary embodiment, and promptly they itself are to have ferromagneticly, and therefore,

magnetic field line

25,26 can penetrate in valve plate 5 and the piston 3.Spacing between piston 3 and the piston hole 2 is shown at this large.

Fig. 9 is presented at the piston-cylinder structure 21 during the asymptotic compression stroke, and piston is on the stroke of the direction of upper dead center.Be arranged in first permanent magnet 11 on the first end face 3a of piston 3 and be embedded in second permanent magnets 12 of the fixed-site in the valve plate 5 near dress.The magnetic field of two

permanent magnets

11,12 is obviously bigger each other than influence in Fig. 8.In working zone 14, the field wire separately 25 of permanent magnet, the spacing between 26 reduce, and it is bigger that magnetic intensity becomes, and field wire is similar to spring by " tensioning ".

According to Figure 10, piston 3 has arrived its upper dead center.Also therefore repel each other owing to two

permanent magnets

11 and 12 point to each other with the pole orientation (with " arctic ") that is equal to separately, strike on the valve plate 5 so prevent the first end face 3a of piston 3.If the exciting field of exciting winding 8 turns at this moment, then piston 3 will the right shift through the repulsive force of

permanent magnet

11,12.

According to according among Fig. 8-10 in the zone of upper dead center the identical basic mode of limited piston stroke, also can be in the zone of lower dead centre the limited piston stroke.

Figure 11 shows power-stroke chart, the increase of the magnetic force when being illustrated in first permanent magnet 11 near second permanent magnet 12.Spacing between first permanent magnet 11 and second permanent magnet 12 is centimetre to be that unit is plotted on the horizontal axis, and magnetic force F is that unit is plotted on the vertical axis with %, wherein 100% be illustrated in upper dead center repulsion magnetic force.This power must be applied by Linear actuator 6 and the mass inertia with piston 3 of oscillating body 7, thereby 3 short time of piston are remained on upper dead center.Provide upper dead center when in this example, the spacing between first permanent magnet 11 and second permanent magnet 12 is for 0.05-0.5mm.Rhombus measuring point and be shown based on the measurement curve that measuring point carries out interpolation.

Figure 12 shows according to the piston cylinder units with double-piston of the present invention.Piston 3 is configured to double-piston and comprises two

piston sections

19,20, and these two piston sections are disposed on the opposed end regions and form an end face 3a, the 3b of double-piston respectively.At the first end face 3a of double-piston and comprise between first cylinder head 4 of first valve plate 5 and form first working space 14, formation second working space 14 ' between the second end face 3b of double-piston and second cylinder head 4 ' that comprises second valve plate 5 '.Oscillating body 7 is disposed between two the

end face

3a, 3b of double-piston, preferably by double-piston 3 sealings.Be provided with according to

permanent magnet layout

11a, 12a or a 11b of the present invention, 12b 4/19 or 4 '/20 to each cylinder head-piston section.

Reference numerals list

1 cylinder baffle

2 piston holes

3 pistons

First end face of 3a piston

Second end face of 3b piston

4 cylinder head

4 ' second cylinder head

5 valve plates

5 ' second valve plate

6 Linear actuators

7 oscillating bodies

8 exciting winding (stator)

9 piston longitudinal axis

11,11a, 11b first permanent magnet

12,12a, 12b second permanent magnet

13 free spaces

The working space of 14 pistons 3

Second working space of 14 ' piston 3

15 suction valves

15 ' second suction valve

16 pressure valve

16 ' second pressure valve

17 suction openings

17' second suction opening

18 pressure openings

The 18' second pressure opening

The first piston section of 19 double-pistons

The second piston section of 20 double-pistons

21 piston cylinder units

22 piston shaft

23 Linearkompressors

The shell of 24 Linear actuators

The field wire of 25 first permanent magnets

The field wire of 26 second permanent magnets

27 spring elements

Claims

1. coolant compressor with closed compressor shell; The piston cylinder units of compressed refrigerant (21) is disposed in the inside of compressor case; The cylinder baffle of piston cylinder units (1) is sealed by cylinder head (4) at end face; In cylinder head, be provided with suction opening (17) and pressure opening (18); Via this suction opening and pressure opening, refrigeration agent is sucked by suction opening via suction valve (15) and is compressed by the pressure opening via pressure valve (16), and wherein piston cylinder units (21) has at least one piston (3) of guiding in the piston hole (2) of cylinder baffle (1); The working space (14) that wherein is used for compressed refrigerant is formed between first end face (3a) of cylinder head (4) and piston (3); Wherein be provided with Linear actuator (6), this Linear actuator (6) comprises at least one oscillating body (7) that is surrounded by exciting winding (8), and this oscillating body (7) is connected to piston (3); So that this piston is moved with vibration mode along the direction of piston longitudinal axis (9)

It is characterized in that; Piston cylinder units (21) is equipped with at least one permanent magnet layout; Said at least one permanent magnet layout comprises respectively being arranged on the piston (3) or being arranged at least one first permanent magnet (11) on the parts that are connected to piston (3) and being arranged in cylinder baffle (1) goes up or is arranged at least one second permanent magnet (12) on the parts that are connected to cylinder baffle (1); Wherein said first permanent magnet (11) always points to each other with identical pole orientation with said second permanent magnet (12); Between two permanent magnets (11,12), producing repulsive interaction, thereby at said first permanent magnet (11) limited piston stroke in the zone at upper dead center and/or in the zone at lower dead centre during near said second permanent magnet (12).

2. coolant compressor according to claim 1; It is characterized in that the said parts that are connected to said at least one first permanent magnet (11) of being furnished with of piston (3) are said oscillating body (7) or are the piston shaft (22) that said piston (3) is connected to said oscillating body (7).

3. coolant compressor according to claim 1 and 2 is characterized in that, the said parts that are connected to said at least one second permanent magnet (12) of being furnished with of cylinder baffle (1) are said cylinder head (4).

4. coolant compressor according to claim 3; It is characterized in that; In said cylinder head (4), arrange valve plate (5); And said at least one second permanent magnet (12) is disposed in that this valve plate (5) is gone up, preferably dress is embedded in this valve plate (5) at least in part, so as in the zone of upper dead center the limited piston stroke.

5. coolant compressor according to claim 1 and 2 is characterized in that, the said parts that are connected to said at least one second permanent magnet (12) of being furnished with of cylinder baffle (1) are for surrounding the shell (24) of said oscillating body (7).

6. according to each described coolant compressor in the claim 1 to 4, it is characterized in that said at least one second permanent magnet (12) is disposed in the inside of the piston hole (2) of cylinder baffle (1).

7. according to each described coolant compressor in the claim 1,3,4,6, it is characterized in that said at least one second permanent magnet (12) is disposed in inside or restraint of labour space (14) of working space (14).

8. according to each described coolant compressor in the claim 1,2,6; It is characterized in that; Said at least one second permanent magnet (12) be disposed in cylinder baffle (1) with the opposed end regions of cylinder head (4) in so that in the zone of upper dead center the limited piston stroke.

9. according to each described coolant compressor in the claim 1,3,4,6,7, it is characterized in that, said at least one first permanent magnet (11) be disposed in piston (3) in the zone of first end face (3a) of cylinder head (4).

10. coolant compressor according to claim 8 is characterized in that, said at least one first permanent magnet (11) is disposed in second end face (3b) away from cylinder head (4) of piston (3) and goes up or be arranged on the piston shaft (22).

11., it is characterized in that said at least one first permanent magnet (11) is partially or even wholly adorned and is embedded in the end face (3a, 3b) and/or in piston shaft (22) according to claim 9 or 10 described coolant compressors.

12. according to claim 4 or 11 described coolant compressors; It is characterized in that; Said permanent magnet (11,12) is adorned in the end face (3a, 3b) that is embedded in piston (3) and/or in the valve plate (5) like this; Make between permanent magnet and piston or valve plate, to have at least one free space (13), this at least one free space is communicated with working space (14).

13. coolant compressor according to claim 12 is characterized in that, said free space (13) is configured to the gap, and the clear opening width in this gap broadens towards the direction of said working space (14).

14., it is characterized in that said groove (13) uses nonferromagnetic material to fill according to claim 12 or 13 described coolant compressors.

15., it is characterized in that said at least one first permanent magnet (11) is arranged to mutually opposed with said at least one second permanent magnet (12) according to each described coolant compressor in the claim 1 to 14.

16. according to each described coolant compressor in the claim 1 to 15; It is characterized in that; Said permanent magnet (11,12) is configured to basic annular; Wherein should annular preferably rotate extension symmetrically, and/or preferably be configured to the annular space according to claim 12 or 13 described free spaces about piston longitudinal axis (9).

17. according to each described coolant compressor in the claim 1 to 16; It is characterized in that the end face (12a) that an end face (11a) of said at least one permanent magnet (11) is basically parallel to said at least one second permanent magnet (12) extends.

18., it is characterized in that said at least one first permanent magnet (11) has the field intensity that equates basically, the preferred basic quality that equates with said at least one second permanent magnet (12) according to each described coolant compressor in the claim 11 to 17.

19. according to each described coolant compressor in the claim 11 to 18; It is characterized in that; A plurality of permanent magnets (11,12) are disposed on the circle that extends with one heart about piston longitudinal axis (9), and the angular separation of wherein adjacent permanent magnet (11,12) is equal basically.

20. according to each described coolant compressor in the claim 1 to 19; It is characterized in that; Said piston (3) is configured to double-piston; Comprise two piston sections (19,20); These two piston sections are arranged on the opposed end regions of said double-piston (3) and form an end face (3a, 3b) of said double-piston respectively; Wherein at first end face (3a) of said double-piston (3) and comprise between first cylinder head (4) of first valve plate (5) and form first working space (14); At second end face (3b) of said double-piston (3) and comprise between second cylinder head (4 ') of second valve plate (5 ') and form second working space (14 '); And wherein said oscillating body (7) is disposed between two end faces (3a, 3b) of said double-piston (3), is preferably surrounded by said double-piston (3), and to each cylinder head-piston section (4/19,4 '/20) is provided with one according to each described permanent magnet layout in the aforementioned claim.

21. one kind is used for confirming that Linearkompressor is in the method according to the piston stroke of the coolant compressor as described in the preamble of claim 1; It is characterized in that; Piston cylinder units (21) is according to each said structure in the claim 1 to 20; And under the situation of given in advance permanent magnet (11,12); Set the drive strength of Linear actuator (6) like this, make piston in given in advance upper dead center and/or lower dead centre, change the movement direction of this piston, and do not use the spring element of machinery.

22. method according to claim 21 is characterized in that, the frequency of confirming of also given in advance Linear actuator (6).

23., it is characterized in that the drive strength of Linear actuator (6) and/or frequency are set based on the position of piston data and/or the magnetic intensity that measure according to claim 21 or 22 described methods.