CN102084132A - Coolant compressor - Google Patents
Coolant compressor Download PDFInfo
- Publication number
- CN102084132A CN102084132A CN2009801241125A CN200980124112A CN102084132A CN 102084132 A CN102084132 A CN 102084132A CN 2009801241125 A CN2009801241125 A CN 2009801241125A CN 200980124112 A CN200980124112 A CN 200980124112A CN 102084132 A CN102084132 A CN 102084132A
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- Prior art keywords
- piston
- cylinder housing
- hole
- work surface
- cylinder
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/122—Cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/121—Casings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B2201/00—Pump parameters
- F04B2201/02—Piston parameters
- F04B2201/0206—Length of piston stroke
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
Disclosed is a hermetically enclosed coolant compressor (1) comprising a cylinder housing (3) and a piston (6) which is guided along a defined piston bearing area (9) within a piston bore (8) of the cylinder housing (3) and is hinged, by means of a connecting rod (7), to a crankshaft (5) that is driven by an electric motor (13). The crankshaft (5) is mounted in a bearing element (2) that is preferably designed in a monolithic manner along with the cylinder housing (3). The piston bore (8) is closed by a cylinder head (15) encompassing a valve disk (16) in a first end region (8a) while being open for accommodating the piston (6) in a second end region (8b) facing the crankshaft (5). According to the invention, the piston bore (8) has a free-running section (10) that adjoins the piston bearing area (9) and is arranged in the second end region (8b) of the piston bore (8). The width (10') of the internal opening of the free-running section (8b) is greater than the diameter (9') of the piston bearing area (9) in order to prevent contact between the piston (6) and the cylinder housing (3) in said section.
Description
Technical field
The present invention relates to a kind of coolant compressor of the enclosed package as described in the preamble according to claim 1, comprise cylinder housing and in the piston hole of cylinder housing along the piston of a definite working surface of piston guiding in order to the compression work medium, described piston by means of rod hinge connection on by electric motor driven bent axle, wherein can be in the supporting mass of preferred and one of cylinder housing formation around the crankshaft support of rotating shaft rotation, piston hole is sealed by a cylinder cap that comprises valve plate on a first end zone, and piston hole opens wide in the face of on the second end zone of bent axle at one, in order to hold piston.
Background technique
It for many years is known utilizing the refrigerator working procedure of non-azeotropic (zeotropen) gas like this.Wherein refrigeration agent heats vaporizer by the power absorption from space to be cooled and is overheated at last, this causes evaporating and is compressed to higher stress level by means of the piston-cylinder-device of coolant compressor, heat discharges via condenser and is sent back to vaporizer again via throttle valve there, carries out the step-down and the cooling of refrigeration agent in described throttle valve.Such coolant compressor is used in field of household appliances and industrial field, and it is arranged on the back side of refrigerator or refrigerating cabinet usually there.
Coolant compressor with compressor housing of airtight sealing comprises motor, and it is via crank-driven pistons reciprocating in the piston hole of cylinder housing, in order to compressed refrigerant.Normally, cylinder housing becomes a form with the supporting mass on the stator that can be fixed on motor to constitute, and this supporting mass has the main bearing that is used to hold bent axle.To this alternately, also cylinder housing can be made for independent member and be fixed on the supporting mass.
The piston hole of cylinder housing seals by valve plate or by cylinder cap on one first axial end region, and piston hole one in the face of opening wide on the second end zone of bent axle, be used to hold piston or under the assembled state of coolant compressor, passed by connecting rod.
In order to reduce the friction of piston during its working stroke as far as possible, satisfactoryly be, keep as far as possible little pistons work surface, that is the surface that contacts with cylinder housing by the piston that piston hole constitutes or (owing to need lubricating film) piston in small gap by the surface of cylinder housing guiding.Therefore piston preferably protrudes from piston hole or piston with its outer surface contact piston working surface partly only at its lower dead point position.
Has requirement with in the producing by batch of a kind of economy of coolant compressor, that is: an above-mentioned cylinder housing or the supporting mass with cylinder housing can be installed in a plurality of coolant compressor product lines, they structurally, particularly the size about the swept volume of piston-cylinder-device is different each other.
In order in cylinder housing, to realize and the output power data of each product line pattern corresponding work volume, be equipped with the piston and the connecting rod of different size for cylinder housing or bent axle.Distinctive selection by (respectively along cylinder shaft centerline measurement) piston length and length of connecting rod is inserted in the piston hole piston different depth.
According to prior art, the distance towards between the origin or beginning of bent axle that remains on the pistons work surface of the rotating shaft of bent axle and cylinder housing does not in this case change, even that is do not change the second end zone of piston hole when connecting rod that uses different length or piston in cylinder housing yet.Adaptive in order to implement the corresponding work space, that shortens piston hole on the contrary for example shortens current oversize cylinder housing by means of milling towards the first end of cylinder cap zone or in being used to support the predetermined zone of cylinder cap or valve plate in the axial direction by means of cutting working method.
Cylinder housing or piston hole are shortened in the second end zone one respectively with the corresponding size of required swept volume after, valve plate is fixed on together with cylinder cap on the end face of last processing of cylinder housing.
But at cylinder cap and valve plate under the situation of special prepackage on the cylinder housing, especially under the situation of the cylinder cap fixing device of the no screw known by EP1888918A1, do not consider the processing or the shortening of the above-mentioned cylinder cap side of cylinder housing, or be counted as uneconomic, because cylinder housing is provided with the fixed groove that cooperation is accurately made in this zone, kayser ground embeds corresponding fixed element in them.
Axial length adaptive also possible that replaces cylinder housing or piston hole is by the adaptive swept volume of making corresponding requirements on piston hole diameter or the whole pistons work surface of setting in cylinder housing.In this case, can enlarge the piston hole diameter and also can pack in the piston hole of counterboring of cylinder housing by counterboring having the corresponding piston of determining piston diameter size or bigger more greatly.But the processing of the piston of these required different size diameter be expend with uneconomic.The accurate final processing of the cooperation of the piston hole of counterboring in the zone on pistons work surface also causes high processing charges.
Summary of the invention
Therefore the objective of the invention is, advise a kind of simple possibility, in order to being implemented in the different swept volume of the cylinder housing that is provided with on the supporting mass, and needn't make piston diameter be matched with required swept volume and needn't carry out cylinder housing or piston hole in the processing/shortening of cylinder cap side.In this case, the friction of piston on the guide surface of piston of cylinder housing reduced to minimum flow and reduce wearing and tearing and power loss thus with a kind of coolant compressor.
Particularly cylinder housing or supporting mass want to be equipped with the piston and the connecting rod of different length, wherein will be with the pistons work surface, that is during its working stroke, nuzzle up that zone structure as small as possible correspondingly of cylinder housing of piston.
Another object of the present invention is that suggestion advantageously assembling makes the wrist pin of piston hinge on connecting rod, so that can realize a large amount of configuration possibilities structurally, in order to implement piston-cylinder-device, special in to determine the size of piston, connecting rod and bent axle.
Achieve the above object by a kind of coolant compressor of the feature with claim 1 characteristic of enclosed package according to the present invention.The piston that coolant compressor of the same type comprises cylinder housing and leads along a definite pistons work surface in the piston hole of cylinder housing, in order to the compression work medium, described piston by means of rod hinge connection on by electric motor driven bent axle, wherein can around the crankshaft support of rotating shaft rotation in preferred and cylinder housing constitute in one the supporting mass and piston hole on a first end zone by valve plate or cylinder cap sealing, and piston hole one face on the second end zone of bent axle be open wide in order to hold piston.Set according to the present invention, piston hole has an idle running part in the face of being provided with in the second end zone of bent axle at piston hole that is adjacent to the pistons work surface, its open interior width is greater than the diameter on pistons work surface, so that preventing during the working position of piston or in the reciprocating motion of the pistons process contacting between this part inner carrier and the cylinder housing.
Therefore the idle running part perpendicular to the cross sectional inner diameter of cylinder shaft centerline measurement or diameter greater than the piston hole diameter in the zone on pistons work surface.Because a corresponding required longitudinal length is reduced to by being provided with according to idle running part of the present invention in the pistons work surface, can reduce the useful horsepower that therefore the unnecessary friction of piston on cylinder housing also improve coolant compressor.At this, piston and the connecting rod that be equipped with different length can for cylinder housing or supporting mass, the pistons work surface of the cylinder housing that in its working stroke, nuzzles up by piston in optimization aspect the friction techniques wherein, that is can make its maintenance as far as possible little.
Another advantage of the present invention is, partly makes and is more prone to from the piston of engage sides cylinder towards bent axle of cylinder by having the compare idle running of big internal diameter of its diameter with the pistons work surface.
Transition between the idle running of cylinder housing part and pistons work surface is made up by means of chamfering, rounding or chamfering-rounding in a kind of embodiment preferred of the present invention and is constituted, and this helps the slip on the pistons work surface of the joint of piston and piston once more.
In a kind of embodiment preferred of the present invention, idle running part with plain mode on the processing technique be configured in cylinder housing with respect to the rotational symmetric groove of cylinder axis.
Set according to a kind of particularly preferred embodiment of the present invention, it is minimum along the direction of cylinder axis or the guiding length of measuring along the axial direction of piston hole that the idle running part is arranged to make the pistons work surface to have in cylinder housing.Under the situation of the guiding length that described minimum is set, piston its lower dead point position only the indentation piston hole with corresponding zone, pistons work surface in so far away, make to stop piston from piston hole, to come off and produce enough seal actions on the relative pistons work of piston surface.Therefore make towards the overlap region of the lower dead point position of piston outer surface that observe, piston and be chosen to especially just in time so greatly with the pistons work surface of cylinder housing, make and to guarantee reliable sealing by the cylinder volume of the end face restriction of piston end face and valve plate, and piston portion protrude from the end regions of the crankshaft side on pistons work surface.
By the pistons work surface being reduced to minimum guide surface and therefore being protruded from guide surface piston portion, the advantage that also draws is, than can use short connecting rod under the situation about being fully retracted of the piston that is in its lower dead point position in the pistons work surface.Its length is chosen to the small construction size that short as far as possible connecting rod can be realized coolant compressor.Possible like this space is saved and also can be used for strengthening the rotor that is connected in bent axle of motor in compressor housing, thereby can access the higher torque of bent axle.
Economic especially the producing by batch and can reach like this of coolant compressor of the same type that is: makes by the cylinder housing of standard manufacture or the working space of supporting mass and can be adapted to size arbitrarily.At this, the idle running part that enlarges the piston hole diameter is provided with in this wise according to corresponding swept volume to be achieved, that limited by valve plate and piston end face in cylinder housing, that is: pistons work surface is corresponding reduces to minimum guiding length, and described swept volume can be determined by changing piston or the position of pistons work surface in piston hole.Supporting mass therefore can be used as the basis of the coolant compressor series that is used to make different structural types by that determine or the not oversize yet cylinder housing of its swept volume of standard manufacture.The cost of production of each member of such coolant compressor series can keep saving very much thus.
The piston hole of making by standard can enlarge by machining according to usage requirement in the face of on the second end zone of bent axle in this wise at it, makes guiding length reduce to corresponding possible minimum value.
Corresponding adaptive such change that can realize piston or the pistons work surface position in piston hole of the geometrical shape by piston-cylinder-device.In a kind of particularly preferred embodiment of the present invention, realize the change of the position on piston or pistons work surface by means of the connecting rod and/or the piston that use (according to corresponding required swept volume) to be specified to the different length size.Be understandable that the length of piston and connecting rod is measured at this vibration-direction along piston.
But also can rod hinge connection be realized the change of position in piston hole on piston or pistons work surface with respect to the eccentricity of the rotating shaft of bent axle at the crank journal on the bent axle by changing.
Do not contact cylinder housing in order to ensure piston in the idle running part, set according to a kind of embodiment preferred of the present invention, the cross sectional inner diameter of idle running part is than the big 2/100mm of piston hole diameter, preferred big 1/10mm.
Set according to another embodiment preferred of the present invention, cylinder housing has and is substantially perpendicular to first mounting hole that the cylinder axis extends, and wherein the medial axis of this mounting hole is arranged to respect to the piston pin axis of the piston that is in its lower dead point position spacing dimension of direction skew towards the first end zone of piston hole.Preferred first mounting hole is used for inserting a reverse setting tool in the piston pin hole and determining the position of wrist pin in piston pin hole thus.But first mounting hole also can be used for wrist pin itself is inserted in the piston pin hole.
Can provide bigger structure interval by wrist pin being installed in the piston above its lower dead point position, in order to the size of each member of determining piston-cylinder-device.Particularly can use the connecting rod and piston and the different bent axle of determining size of different length, wherein always can implement the optimization on friction techniques on pistons work surface by above-mentioned idle running part according to setting of the present invention.
Description of drawings
Illustrate in greater detail the present invention by embodiment now.Wherein:
Fig. 1 is according to the sectional view of coolant compressor of the present invention,
Fig. 2 makes the parts drawing that waits axle of one supporting mass according to of the present invention and cylinder housing,
Fig. 3 is according to the vertical cross section of the supporting mass of Fig. 2 of the present invention,
Fig. 4 is according to the plan view of the supporting mass of Fig. 2 of the present invention,
Fig. 5 is according to the bottom view of the supporting mass of Fig. 2 of the present invention,
Fig. 6 is according to the side view of the supporting mass of Fig. 2 of the present invention,
Fig. 7 has the plan view of the supporting mass of bigger swept volume, and the piston that wherein leads in piston hole is in its lower dead point position,
Fig. 8 presses the sectional view of the supporting mass A-A intercepting along the line of Fig. 7,
Fig. 9 has the plan view of the supporting mass of less swept volume, and wherein the piston in the piston hole guiding is in its lower dead point position,
Figure 10 presses the sectional view of the supporting mass A-A intercepting along the line of Fig. 9,
Thin portion " A " among Figure 11 Figure 10.
Embodiment
The compressor housing 14 that comprises airtight sealing shown in Fig. 1 according to coolant compressor of the present invention.Motor 13 in the bottom section that is bearing in compressor housing 14 by means of the rubber-like bearing device is set in compressor housing 14.
Lay the supporting mass 2 of a bridge shape on motor 13, it is fixed on the stator 13a of motor 13 by means of screw element 29.At Fig. 2 with the supporting mass shown in the parts drawing 2 across the top of the motor winding 34 of motor 13 (being also referred to as " going up winding overhang ") and have two mutual opposed feet elements 31 and 32, they are bearing on the stator 13a.Each feet elements 31,32 has two bearing 31a, 31b or 32a, 32b at end face, (sees the bottom view by Fig. 5 supporting mass 2) thereby therefore the supporting mass of narrower formation 2 stably is bearing on the stator 13a on four supporting surfaces altogether.
Each feet elements 31,32 is provided with tapped hole 33.The stator 13a of motor 13 is provided with the through hole 30 that perpendicular is extended on the working position of coolant compressor 1, and screw element 29 can be passed them and also can be tightened in the tapped hole 33 of supporting mass 2.The screw head 29a of the bottom section of facing compressor housing 14 of screw element 29 inserts to have in the bearing device 27 of elasticity (gefederte), thereby motor 13 is remained in the corresponding required working position together with fixing thereon supporting mass 2.
Supporting mass 2 is configured to 3 one-tenth one of cylinder housing, described cylinder housing is used for being contained in the piston 6 of piston hole 8 guiding of cylinder housing 3, compresses via input in known manner and discharge conduit 35 enters in the compressor housing and the refrigeration agent of derivation from compressor housing 14 again by means of it.
To be used to hold the form that bent axle 5 is provided be the main bearing 4 of sliding bearing at one of the core 2a structure between the feet elements 31,32 of being in of supporting mass 2.The rotating shaft 11 of bent axle 5 or the axis of symmetry of sleeve shape main bearing extend (see figure 3) perpendicular to cylinder axis 12.
The axle 5a of bent axle 5 be connected in rotor 13b and by corresponding stator commutate (Stator-Kommutierung) be in rotation, thereby be hinged on piston 6 on the bent axle 5 along 12 to-and-fro motion of cylinder axis by means of connecting rod 7.
At this, connecting rod 7 have a first end part that is provided with first connecting rod hole 7a and one be provided with second connecting rod hole 7b the second end part, and the shaft portion 7c that interconnects this two end part part.First connecting rod hole 7a is hinged on the crank journal 19 of eccentric wheel 18 of bent axle 5, and second connecting rod hole 7b is hinged on the piston 6 by means of link pin 23.
The piston hole 8 of cylinder housing is sealed by valve plate 16 at first end zone 8a, and piston hole 8 on the second end zone 8b be in the face of bent axle 5 open wide in order to hold piston 6 or to pass through by connecting rod 7.
Piston 6 carries out corresponding definite piston stroke x in piston hole 8, wherein Yi Xia stroke is understood that piston stroke x, that is: piston 6 towards the end face 6a of valve plate 16 during the working stroke or from the lower dead point position of piston 6 to the stroke that moves the moving period of its upper dead center position.
Pre-install such cylinder cap device in batches and should no longer change, the zone of the cylinder side of milling cylinder housing 3 afterwards not particularly, just as being implemented for the swept volume of cylinder housing 3 changes usually.
The length of the piston 6 that does not rely on the length of connecting rod 7 and measure along the vibration-direction of piston 6, that is do not rely on piston 6 and during its working stroke, enter in the piston hole 8 how deeply, should reduce the friction of piston 6 in cylinder housing 3 as far as possible, this optimization of the frictional behaviour of piston 6 reaches in this wise, that is: keep as far as possible little pistons work surface 9, it is that surface that is made of piston hole 8, piston 6 contacts cylinder housings 3 or nuzzles up under the situation in small gap thereon, thereby piston 6 protrudes from piston hole 8 or pistons work surface 9 at it piecemeal at the lower dead point position shown in Fig. 7 and 8.In only exemplary mode the piston 6 that is in its lower dead point position is shown among Fig. 8, its outer surface only surrounds about 3/4ths cylinder hole 8 or pistons work surface 9, and outer surface of piston about 1/4th protrude from cylinder hole 8, that is can't help cylinder housing 3 guiding.
The swept volume that is provided with in cylinder housing 3 for the end face that changes by (unshowned in Fig. 8) valve plate 16 and piston 6 limits has a plurality of structural possibilities.Can determine swept volume by means of the change of position or pistons work surface 9 position in piston hole 8 of piston 6 according to the characteristic of corresponding refrigerating agent compressor arrangement pattern.
Preferably, change the position on swept volume or piston 6/ pistons work surface 9 by the length that changes connecting rod 7 or pitman shaft 7c.
The change of the position on the swept volume of the piston-cylinder shown in Fig. 8-device 28 or piston 6/ pistons work surface 9 also can realize by following measure, that is: change the geometrical shape of bent axle 5, for example strengthen reduce the eccentricity of crank journal 19 or the axis 20 of the crank journal 19 that on eccentric 18, is provided with respect to the distance of the rotating shaft 11 of bent axle 6.Also change the length of piston stroke x in this case.
Similarly, can be by revising piston geometry or realizing the change of the position on swept volume or piston 6/ pistons work surface 9 by changing (being parallel to cylinder axis 12 measurements) piston length.
Do not rely on the change which concrete member to revise the implementation volume by, the pistons work surface 9 in cylinder hole 8 also is offset or is similar to the change of swept volume with its shortening or lengthening.
Only exemplary piston-cylinder-device 28 with longitudinal length z of the bigger swept volume of measuring along cylinder axis 12 shown in Figure 8, and the piston-cylinder apparatus 28 with less swept volume longitudinal length z along 12 measurements of cylinder axis shown in Figure 10.
If for example change longitudinal length z in the swept volume of the piston-cylinder shown in Fig. 8-device 28, the axis 20 of the feasible crank journal 19 that can use long connecting rod 7 and be provided with on eccentric wheel 18 also is matched with bent axle 5 to the spacing of the rotating shaft 11 of bent axle 5, then the result of its generation is, even piston 6 also enters in the piston hole 8 when its lower dead point position and the whole outer surface of being surrounded pistons 6 in this case by piston hole 8 more deeply.
Certainly, still also can be by correspondingly changing piston hole diameter 8 ' or be implemented in the modification or the expansion of the swept volumes that are provided with in the cylinder housing 3 by counterboring piston hole 8.
But as beginning is described, is being disadvantageous aspect the friction efficiency by the whole outer surface of piston of cylinder housing 3 contact, because if 6 in piston is partly in the piston hole 8 of indentation cylinder housing 3, it is enough at the lower dead point position of piston 6.
Set according to the present invention, piston hole 8 have one be adjacent to pistons work surface 9, piston hole 8 in the face of the second end of bent axle 5 zone 8b in the idle running part 10 that is provided with, its open interior width or its diameter 10 ' greater than the diameter 9 on pistons work surface 9 '.
The diameter 8 of piston hole 8 ' or the diameter on pistons work surface 9 therefore in the 8b of the second end zone, widened (seeing Figure 10 and Figure 11) by idle running part 10, in this idle running part, do not contact cylinder housing 2 in the process of the reciprocating motion of the pistons that piston 6 is implemented under its working state.
Can for example be configured to the groove (in Figure 10 or Figure 11, being visible like this) that rotation in cylinder housing 3 is symmetrical in cylinder axis 12 according to idle running part 10 of the present invention.
Replace of the concentric setting of idle running part 10 with respect to piston hole 8, also can implement idle running part 10 any other setting and how much form of implementation.Idle running part 10 also can be configured to the chamfering on the inner face corresponding with piston hole 8 of cylinder housing 3.
In any case piston hole 8 has the part of an expansion in the face of the second end of bent axle 5 zone 8b, its cross sectional inner diameter 10 ' greater than the piston hole diameter 8 in the zone on pistons work surface 9 ' or greater than pistons work surface diameter 9 '.
Idle running part 10 preferably is arranged in the cylinder housing 3 in this wise, that is: make pistons work surface 9 have minimum (along the reciprocating motion of the pistons direction or be parallel to cylinder axis 12 measures) guiding length.Under the situation of the guiding length of such minimum, piston 6 indentation in the pistons work surface 9 corresponding zone of its lower dead point position at piston hole 8 is so far away, make to stop piston 6 from piston hole 8, come off and produces enough seal actions on piston 6 relative pistons work surfaces 9, so guarantee the reliable sealing of the cylinder volume that end face 6a and valve plate 16 by piston 6 limit.Half axial length protrudes from pistons work surface 9 with it as long as piston 6 is in its lower dead point position maximum, just stops piston 6 to come off from piston hole 8.
By being provided with according to idle running part 10 of the present invention, to or be parallel to the longitudinal length 10 that pistons work surface 9 is measured along the vibration-direction of piston 6 " therefore be chosen to minimum guiding length is reduced on pistons work surface 9, so the outer surface of piston 6 partly exposes again at the lower dead point position of piston.In pressing the piston-cylinder of Figure 10-device 28, wherein piston 6 enters in the piston hole 8 and the first end zone 8a of the cylinder cap side in 9 abuts piston holes 8, pistons work surface more deeply, therefore draw as by the advantage on the friction techniques identical in being provided with of Fig. 8, wherein protrude from cylinder housing 3 the second end zone 8b of pistons work surface 9 overlapping piston holes 8 and piston portion.
Therefore the spacing basis towards the origin or beginning of bent axle 3 to the rotating shaft 11 of bent axle 3 on pistons work surface 9 according to the location of idle running part 10 of the present invention no longer (as in the prior art) be constant, but variable.
Therefore possible, for the different swept volume of a plurality of refrigerating agent compressor arrangement patterns that differ from one another by its piston-cylinder-device 28 provides the standard supporting mass 2 determining oversize cylinder housing 3 about its axis vertical length or have such cylinder housing 3.Can be with other order adaptive in this wise cylinder housing 3 or supporting mass 2 respectively, that is: the outer surface of piston 6 partly exposes by the idle running part or it reduces to minimum guiding length with pistons work surface 9 at its lower dead point position.
Should illustrate, save the cylinder cap 15 that in the 8a of the first end of piston hole 9 zone, is provided with and the view of valve plate 16.
Can realize the manufacturing of idle running part 10 or the expansion of piston hole 8 by for example boring of cutting working method, turning or the milling that is fit to.Preferably idle running part 10 is made the diameter of increasing by the simple counterboring of piston hole 8.
At this, the cross sectional inner diameter 10 of idle running part 10 ' than piston hole diameter 8 ' big 2/100mm, preferred big 1/10mm.Cross sectional inner diameter 10 by idle running part 10 ' than piston hole diameter 8 ' preferred big 1mm can be from the side of the second end zone 8b of the crankshaft side of piston hole 8 be packed piston 6 into cylinder housing 3 simply.
In addition, help piston 6 from cylinder housing 3 is packed in the second end zone of piston hole into by being configured with of the corresponding transition between the pistons work surface 9 of idle running part 10 and cylinder housing 3.Such transition preferably constitutes by means of (being shown in broken lines at the detail drawing by a Figure 11) chamfering 38 or rounding 39.Chamfering 38 or rounding 39 preferably are concentric with cylinder axis 12 and extend.
Should illustrate that cylinder housing 3 also can constitute multi-part type, so that reach the advantage that processing is saved.Can for example be provided with like this to holding the inserts that piston 6 is provided with, their insert, preferably are pressed in corresponding (along cylinder axis 12) groove in the cylinder housing 3 and maybe can also fix by the technique for fixing of another kind of mode.Can relate to for example columniform sleeve in these inserts, its axial length dimension is definite like this, makes it possible to achieve all above-mentioned and in the structure according to piston-cylinder apparatus 28 of the present invention shown in Fig. 1-11.These inserts have the hole of (extend along cylinder axis 12 mounting point in cylinder housing 3), constitute pistons work surface 9 by it.Inserts can or only constitute pistons work surface 8 or also constitutes idle running part 10, therefore can have the sudden change of corresponding transition or ladder.
The above-mentioned particularly advantageous installation of wrist pin 23 in the corresponding piston pin-and-hole 22 of piston 6 that piston 6 is hinged on the connecting rod 7 reaches like this, that is: piston 23 is inserted into (see figure 1) in the piston pin hole 22 at a piston 6 on the position that its lower dead point position moves towards the direction of cylinder cap 15.
In this case, cylinder housing 3 has be substantially perpendicular to first mounting hole 24 that can preferably find out that cylinder axis 12 extends in Fig. 3, and wherein the medial axis 25 of this first mounting hole 24 is arranged to respect to the piston pin axis 21 of the piston 6 that is in its lower dead point position towards the direction of the first end zone 8a of the piston hole 8 spacing dimension y (being shown among Fig. 1) that setovers.
In this first mounting hole 24, can insert unshowned reverse setting tool (Gegenhaltewerkzeug), one directly is inserted in the piston pin hole 22 up to the corresponding required degree of depth or end position, and a backstop is provided on this end position, is used for being inserted into the wrist pin 23 of the second connecting rod hole 7b of piston pin hole 22 and connecting rod 7 from the opposed side of cylinder housing 3.In this case, connecting rod 7 or its second connecting rod hole 7b are retracted within the connecting rod groove 36 that is provided with in the piston 6.
By the reverse setting tool that inserts in first mounting hole 24 or the piston pin hole piston 6 is fixed on the position in the cylinder housing 3, on this position, piston pin axis 21 can insert or be pressed into its working position by Fig. 3 with wrist pin 23 from second mounting hole 37 cylinder housing 3 that is opposite to first mounting hole 24 in alignment with the axis 25 of first mounting hole 24.The backstop that is made of reverse setting tool still needs for this reason, so that utilize (optional be provided with unshowned) fixing pin to be fixed on its working position wrist pin 23.
Second mounting hole 37 can relate to the through hole in cylinder housing 3 that extends perpendicular to cylinder axis 12 or also can relate to other hole arbitrarily.Should illustrate that first mounting hole 24 also can be used for wrist pin 23 is inserted in the piston pin hole 22.
In a piston 6 above its lower dead point position, can provide bigger structure interval by wrist pin 23, be used for structurally constructing piston-cylinder-device 28 or be used for being provided with according to idle running part 10 of the present invention and pistons work surface 9 at cylinder housing 3 according to installation of the present invention.
List of numerals
1 coolant compressor
2 supporting masses
3 cylinder housings
The base bearing of 4 bent axles
5 bent axles
6 pistons
The 6a piston end surface
6 ' piston length
7 connecting rods
7a first connecting rod hole
7b second connecting rod hole
The shaft portion of 7c connecting rod
8 piston holes
The first end zone of 8a piston hole
The second end zone of 8b piston hole
8 ' piston hole diameter
9 pistons work surfaces
9 ' pistons work surface diameter
10 idle running parts
The open interior width of 10 ' idle running part
10 " longitudinal length of idle running part
11 crankshaft center lines
12 cylinder axis
13 motor
The 13a stator
The 13b rotor
14 compressor housings
15 cylinder caps
16 valve plates
The fixed element of 17 cylinder caps
18 eccentric wheels
19 crankshaft journals
The axis of 20 crank journals
21 piston pin axis
22 piston pin holes
23 wrist pins
24 first mounting holes
The axis of 25 mounting holes
26 fixed elements
The bearing device of 27 motor
28 piston-cylinder-devices
29 screw element
30 through holes
31 first feet elements
First bearing of 31a first feet elements
Second bearing of 31b first feet elements
32 second feet elements
First bearing of 32a second feet elements
Second bearing of 32b second feet elements
33 tapped holes
The last winding overhang of 34 motor windings
35 input and discharge conduits
36 connecting rod grooves
37 second mounting holes
38 chamferings
39 roundings
The x piston stroke
Y is in the medial axis 25 of mounting hole 24 and the spacing between the piston hole axis 21
The longitudinal length of z swept volume
Claims (9)
1. the coolant compressor of enclosed package (1) comprising:
Cylinder housing (3), and
Along definite pistons work surface (a 9) guiding, in order to the compression work medium, described piston is hinged on by means of connecting rod (7) on the bent axle (5) that is driven by motor (13) in the piston hole (8) of cylinder housing (3) for piston (6), described piston,
Wherein can be bearing in the supporting mass (2) around the bent axle (5) of a rotating shaft (11) rotation, described supporting mass preferably is configured to one with cylinder housing (3), and piston hole (8) is gone up cylinder cap (15) sealing that comprises valve plate (16) by in a first end zone (8a), and piston hole (8) one in the face of on the second end zone (8b) of bent axle (5) be open wide in order to hold piston (6);
It is characterized in that, piston hole (8) has one and be adjacent to idle running part (10) pistons work surface (9), that be provided with in the second end zone (8b) of the piston hole (8) of facing bent axle (5), the open interior width (10 ') of this idle running part is greater than the diameter (9 ') of pistons work surface (9), so that preventing during the working position of piston (6) contacting between this idle running part inner carrier (6) and the cylinder housing (3).
2. according to the coolant compressor (1) of the described enclosed package of claim 1, it is characterized in that idle running part (10) is configured to respect to the rotational symmetric groove of cylinder axis (12) in cylinder housing (3).
3. according to the coolant compressor (1) of claim 1 or 2 described enclosed package, it is characterized in that, idle running part (10) is arranged to make pistons work surface (9) to have the guiding length along the minimum of the orientation measurement of cylinder axis (12) in cylinder housing (3), wherein piston (6) its lower dead point position piston hole (8) corresponding to the zone of pistons work surface (9) in an indentation so far away, make to stop piston (6) from piston hole (8), come off and produce the seal action on the relative pistons work surface (9) of piston (6).
4. according to the coolant compressor (1) of the described enclosed package of claim 3, it is characterized in that, idle running part (10) is arranged so that according to corresponding swept volume to be achieved, that limited by the end face (6a) of valve plate (16) and piston (6) cylinder housing (3) in pistons work surface (9) reduces to the guiding length of minimum, and described swept volume can be determined by change piston (6) or pistons work surface (9) position in piston hole (8).
5. according to the coolant compressor (1) of the described enclosed package of claim 4, it is characterized in that the connecting rod (7) and/or the piston (6) that are designed to the different length size by means of use are realized the change of piston (6) or pistons work surface (9) position in piston hole (8).
6. according to the coolant compressor (1) of claim 4 or 5 described enclosed package, it is characterized in that, realize the change of piston (6) or pistons work surface (9) position in piston hole (8) with respect to the eccentricity of the rotating shaft (11) of bent axle (3) by the crank journal (19) that change connecting rod (7) is hinged on the bent axle (3).
7. according to the coolant compressor (1) of one of claim 1 to 6 described enclosed package, it is characterized in that the cross sectional inner diameter (10 ') of idle running part (10) is than the big 1/100mm of piston hole diameter (8 '), preferred big 1/10mm.
8. according to the coolant compressor (1) of one of claim 1 to 7 described enclosed package, it is characterized in that pistons work surface (9) are described idle running part (10) by means of chamfering (38) or rounding (39) transition.
9. according to the coolant compressor (1) of one of claim 1 to 8 described enclosed package, it is characterized in that, cylinder housing (3) has and is substantially perpendicular to first mounting hole (24) that cylinder axis (12) extends, and wherein the medial axis (25) of this first mounting hole (24) is arranged to respect to the piston pin axis (21) of the piston that is positioned at its lower dead point position (6) the direction biasing spacing dimension (y) towards the first end zone of piston hole (8) (8a).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT0027508U AT10913U1 (en) | 2008-05-13 | 2008-05-13 | REFRIGERANT COMPRESSOR |
| ATGM275/2008 | 2008-05-13 | ||
| PCT/AT2009/000197 WO2009137857A1 (en) | 2008-05-13 | 2009-05-13 | Coolant compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102084132A true CN102084132A (en) | 2011-06-01 |
| CN102084132B CN102084132B (en) | 2016-07-06 |
Family
ID=40907143
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN200980124112.5A Active CN102084132B (en) | 2008-05-13 | 2009-05-13 | Coolant compressor |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20110123373A1 (en) |
| EP (1) | EP2310682B1 (en) |
| CN (1) | CN102084132B (en) |
| AT (1) | AT10913U1 (en) |
| WO (1) | WO2009137857A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103857911A (en) * | 2011-08-30 | 2014-06-11 | 惠而浦股份有限公司 | Compressor block |
| CN107218220A (en) * | 2017-07-28 | 2017-09-29 | 安徽美芝制冷设备有限公司 | Compressor |
| CN108266350A (en) * | 2017-12-20 | 2018-07-10 | 广州万宝集团压缩机有限公司 | A kind of refrigeration compressor circle cylinder head component |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108302003B (en) * | 2018-04-08 | 2024-02-06 | 黄石东贝压缩机有限公司 | Synchronous double-cylinder refrigeration compressor |
| JP7079174B2 (en) * | 2018-08-29 | 2022-06-01 | ジーエムシーシー アンド ウェリング アプライアンス コンポーネント （タイランド） カンパニー リミテッド | Compressor and equipment using it |
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| GB2190151A (en) * | 1986-05-02 | 1987-11-11 | Brasil Compressores Sa | Silencing and reducing heat absorption in compressors |
| GB2191964A (en) * | 1986-06-26 | 1987-12-31 | Lec Refrigeration Public Limit | Reciprocating piston compressor manufacture |
| CN1067097A (en) * | 1991-05-28 | 1992-12-16 | 巴西船用压缩机有限公司 | The suction muffler assembly of hermetic compressors |
| EP0496151B1 (en) * | 1991-01-22 | 1997-03-05 | Matsushita Refrigeration Company | Hermetically sealed compressor |
| WO2002008606A1 (en) * | 2000-07-19 | 2002-01-31 | Verdichter Oe. Ges.M.B.H. | Method for producing compressor assemblies |
| AT8401U1 (en) * | 2005-03-31 | 2006-07-15 | Acc Austria Gmbh | REFRIGERANT COMPRESSOR |
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| US2740578A (en) * | 1953-02-24 | 1956-04-03 | Avco Mfg Corp | Refrigeration compressor |
| US4406590A (en) * | 1980-06-11 | 1983-09-27 | Tecumseh Products Company | Hermetic compressor |
| US4494286A (en) * | 1982-10-25 | 1985-01-22 | Tecumseh Products Company | Connecting rod arrangement |
| US5118263A (en) * | 1990-04-27 | 1992-06-02 | Fritchman Jack F | Hermetic refrigeration compressor |
| KR0154447B1 (en) * | 1995-11-09 | 1999-03-20 | 김광호 | Reciprocating compressor |
| JP2001193550A (en) * | 2000-01-12 | 2001-07-17 | Kioritz Corp | Cylinder and method for manufacturing same |
| AT413233B (en) * | 2000-07-03 | 2005-12-15 | Verdichter Oe Ges M B H | PISTON RELEASE |
| KR100432714B1 (en) * | 2000-12-06 | 2004-05-24 | 주식회사 엘지이아이 | surface treatment method of sliding parts for hermetic compressor |
| CN1300460C (en) * | 2001-06-01 | 2007-02-14 | Lg电子株式会社 | Dual capacity compressor |
-
2008
- 2008-05-13 AT AT0027508U patent/AT10913U1/en not_active IP Right Cessation
-
2009
- 2009-05-13 EP EP09745279.1A patent/EP2310682B1/en active Active
- 2009-05-13 CN CN200980124112.5A patent/CN102084132B/en active Active
- 2009-05-13 WO PCT/AT2009/000197 patent/WO2009137857A1/en active Application Filing
- 2009-05-13 US US12/992,523 patent/US20110123373A1/en not_active Abandoned
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2190151A (en) * | 1986-05-02 | 1987-11-11 | Brasil Compressores Sa | Silencing and reducing heat absorption in compressors |
| GB2191964A (en) * | 1986-06-26 | 1987-12-31 | Lec Refrigeration Public Limit | Reciprocating piston compressor manufacture |
| EP0496151B1 (en) * | 1991-01-22 | 1997-03-05 | Matsushita Refrigeration Company | Hermetically sealed compressor |
| CN1067097A (en) * | 1991-05-28 | 1992-12-16 | 巴西船用压缩机有限公司 | The suction muffler assembly of hermetic compressors |
| WO2002008606A1 (en) * | 2000-07-19 | 2002-01-31 | Verdichter Oe. Ges.M.B.H. | Method for producing compressor assemblies |
| AT8401U1 (en) * | 2005-03-31 | 2006-07-15 | Acc Austria Gmbh | REFRIGERANT COMPRESSOR |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103857911A (en) * | 2011-08-30 | 2014-06-11 | 惠而浦股份有限公司 | Compressor block |
| CN107218220A (en) * | 2017-07-28 | 2017-09-29 | 安徽美芝制冷设备有限公司 | Compressor |
| CN107218220B (en) * | 2017-07-28 | 2019-04-26 | 安徽美芝制冷设备有限公司 | Compressor |
| CN108266350A (en) * | 2017-12-20 | 2018-07-10 | 广州万宝集团压缩机有限公司 | A kind of refrigeration compressor circle cylinder head component |
| CN108266350B (en) * | 2017-12-20 | 2019-06-04 | 广州万宝集团压缩机有限公司 | A kind of refrigeration compressor circle cylinder head component |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2310682A1 (en) | 2011-04-20 |
| WO2009137857A1 (en) | 2009-11-19 |
| AT10913U1 (en) | 2009-12-15 |
| EP2310682B1 (en) | 2017-04-12 |
| US20110123373A1 (en) | 2011-05-26 |
| CN102084132B (en) | 2016-07-06 |
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