EP1864021B1 - Refrigeration compressor - Google Patents

Description

FIELD OF THE INVENTION

The present invention relates to a hermetically sealed refrigerant compressor with a hermetically sealed compressor housing, in the interior of which a refrigerant-compressing piston-cylinder unit operates, whose cylinder is closed by means of a pressure bore and a suction bore having valve plate and a suction channel and a pressure channel are provided via which refrigerant is sucked via a suction valve into the suction bore and is compressed via a pressure valve from the pressure bore into the pressure channel, wherein a suction muffler is preferably arranged in the suction channel according to the preamble of claim 1.

Such refrigerant compressors have long been known and are mainly used in refrigerators or shelves. Accordingly high is the annually produced quantity.

Although the energy consumption of a single refrigerant compressor is only between 50 and 150 watts, when considering all refrigerating compressors in use worldwide, a very high energy consumption results, which steadily increases due to the rapid development of so-called developing countries.

Any technical improvement that is made to a refrigerant compressor and increases its efficiency, thus, on the global refrigeration compressor in use, has an enormous energy saving potential.

STATE OF THE ART

The refrigerant process as such has long been known. The boiling refrigerant is vaporized by energy absorption from the space to be cooled in the evaporator and finally superheated and pumped by the refrigerant compressor to a higher energy level, where it emits heat through a condenser and via a throttle, in which a pressure reduction and the cooling of the refrigerant , is transported back to the evaporator.

The biggest and most important potential for a possible improvement in the efficiency lies in the lowering of the temperature of the refrigerant at the beginning of its compression process so when sucking into the cylinder of the piston-cylinder unit. Each reduction of this so-called suction temperature therefore causes as well as the lowering of the temperature during the compression process and, associated with the Ausschiebetemperatur a reduction in the required work for the compression process.

In known hermetic refrigerant compressors according to the prior art is due to design a strong heating of the refrigerant on its way from the evaporator (refrigerator) to the intake valve of the piston-cylinder unit.

The suction of the refrigerant via a directly coming from the evaporator suction during an intake stroke of the piston-cylinder unit. From this suction duct, the refrigerant is sucked via a suction muffler and a suction valve into the interior of the cylinder, where it is compressed by the piston and pushed out via a pressure valve from the interior of the cylinder in a pressure chamber leading to the cooling chamber. Known refrigerant compressors have a structure in which the piston housing the cylinder housing through a suction or pressure hole having the valve plate is completed. The valve plate serves as a seat for a cylinder cover, which is usually bolted to the valve plate and the cylinder housing. The cylinder cover has intermediate walls which divide the cavity between the cylinder cover and the valve plate into chambers, which subsequently form the suction or pressure channel, via which the refrigerant is sucked into the cylinder or pushed out of it.

The suction channel usually opens directly into the interior of the hermetically sealed compressor housing in the vicinity of the inlet opening in a suction muffler, which reduces the intake noise of the piston-cylinder unit and is usually constructed of a plurality of interconnected volumes, as well as having the aforementioned inlet opening and an outlet opening which bears tightly against the suction bore of the valve plate.

The described known variant embodiment has the disadvantage that the refrigerant heats up too strongly on its way from the inlet to the interior of the compressor housing to the suction bore. Measurements have shown that between a point in the suction channel shortly before entering the compressor housing and the first volume of the suction muffler, a heating by more than 20 ° C takes place. The main cause of this undesirable heating of the refrigerant is the fact that the fresh refrigerant flowing from the suction channel into the compressor housing is mixed with refrigerant already present in the compressor housing. However, this has due to the output from the piston-cylinder unit heat during operation, a higher temperature than the refrigerant flowing from the suction channel in the compressor housing refrigerant, so that when mixing the two refrigerant streams adjusts a mixing temperature, which is certainly higher than the temperature of the Refrigerant in the suction channel before entering the Compressor housing. The cause of the mixture is the fact that the seated on the valve plate, the suction hole alternately occlusive and releasing intake valve releases the suction only over a crankshaft angle range of 180 ° and therefore only within this time window refrigerant can be sucked into the cylinder of the piston-cylinder unit. While the intake valve is closed during the other 180 ° crankshaft angle range, the compression cycle, the refrigerant coming from the evaporator has an almost constant mass flow, so that it flows into the compressor housing even with the suction valve closed and lingers and cools the piston-cylinder unit and warmed up. In addition, due to the pressure oscillations during the compression phase, further flow processes from the compressor housing to the suction silencer and vice versa, whereby an additional mixing of the refrigerant is effected.

In addition to the mentioned confluence of the suction tube in the compressor housing in the vicinity of the inlet opening in the suction muffler and variants are known, for example from the WO 03/038280 , in which the suction channel is passed directly, without detouring the inside of the compressor housing, into the suction muffler. In this way, leading to the heating of the refrigerant at the beginning of the compression process mixing of the refrigerant flows can not take place. However, this solution has the disadvantage that it usually comes to a larger pressure drop during suction, which reduces the degree of delivery and thus the energy efficiency more or less.

Any known refrigerant compressor in any case have an identical structure of the piston-cylinder unit, in particular of the cylinder housing, which is closed with a valve plate and an adjoining cylinder cover. The cylinder cover preferably covers the entire Valve plate from which also has the suction hole and the pressure hole. On the valve plate and the suction hole temporarily closing suction valve and the pressure bore temporarily occluding pressure valve are arranged. The cylinder cover is usually provided with a recess for the suction channel, or for the end portion of the suction muffler, which opens into the suction hole.

The heated by the compression process refrigerant is forced through the pressure valve and the pressure bore from the cylinder in the cylinder cover, where it due to the construction of the cylinder cover this at least in the pressure channel forming portion, fully fills and thus with the part of this pressure channel forming valve plate , come in contact. The temperature of the valve plate corresponds due to this fact substantially the temperature of the compressed refrigerant. Since the gas in the interior of the cylinder over more than 300 ° crank angle is colder than the valve plate, there is a heat flow from directly the valve plate or indirectly from the valve plate to the cylinder wall and from there to the gas inside the cylinder, which adversely affects the Energy efficiency.

Furthermore, the high temperature prevailing in the cylinder cover also causes a heat flow in the direction of the end section of the suction muffler, which is indeed surrounded by the cylinder cover, whereby, however, the refrigerant coming from the suction muffler, which is still to be compressed, is also undesirably heated. In summary, it can thus be said that the known refrigerant compressor constructions due to their cylinder cover construction of the initially mentioned objective, namely a reduction of the suction temperature and the Ausschiebetemperatur run counter.

From the US 5,288,212 is a hermetically sealed compressor with a arranged on a base plate on the cylinder head suction housing and a separate from this pressure housing known. The same base plate forms the common bottom of suction and pressure housing and lies flat on the cylinder head assembly.

PRESENTATION OF THE INVENTION

It is therefore an object of the present invention to avoid the disadvantages described and to provide a refrigerant compressor of the type mentioned, which allows a significant reduction of the suction temperature and the Ausschiebetemperatur.

This is made possible by the characterizing features of claim 1 according to the invention.

By providing an independent component, which forms the pressure channel and this completely sheathed and direct connection of these components with the pressure bore is carried out a complete thermal separation of the pressure channel of the valve plate. The components according to the invention enable the direct, compressed refrigerant to escape directly via the pressure bore into the pressure channel without having to flow off along a section of the valve plate. Only the region of the valve plate which directly surrounds the pressure bore comes into contact with the hot refrigerant at its side facing away from the piston. As a result, the heat transfer from the hot, already compressed refrigerant to the valve plate over conventional cylinder heads in refrigerant compressors can be drastically reduced. The valve plate and the cylinder wall remain cooler and thereby allow a dissipation of heat from the interior of the cylinder housing, or prevent the inflow of heat into the gas in the cylinder. Furthermore, this way too the heat transfer from the valve plate to the suction hole and thus be reduced in the suction channel, whereby the intake temperature can be lowered.

By the characterizing features of claim 2, that portion of the pressure channel which impinges on the valve plate, that is, that portion which lies within the pressure contact edge, can be accurately dimensioned and optimized with respect to heat transfer. It is necessary on the one hand, that the pressure bore is within this range and on the other hand, the transition between the pressure channel and the pressure bore is formed aerodynamically and still allows a tight connection. Since according to the invention, the pressure channel or more precisely the last portion of these channels substantially perpendicular to the pressure bore and thus impinges on the valve plate to prevent heat transfer from the valve plate to the pressure channel or vice versa, the shape of the pressure contact edge can be chosen so that the refrigerant flows around the valve plate only along a small area.

According to the invention, it is provided that the ratio of the cross-sectional area of the pressure bore to the area enclosed by the pressure-contact edge is more than 1/12.

According to the characterizing features of claim 4, the component forming the pressure channel has a directly adjoining the pressure bore, leading away from the valve plate section and an adjoining this section further section, relative to the cylinder bore radially outwards, preferably at a distance from the valve plate preferably runs parallel thereto. As a result, the compressed refrigerant can be quickly transported away from the valve plate and its heat output to the valve plate can be prevented or reduced.

According to the characterizing features of claim 5, it is provided that the portion leading away from the valve plate and / or the further portion of the pressure channel is made of poorly conductive plastic, whereby the heat output of the compressed refrigerant can be further reduced.

According to the characterizing features of claim 6 is further provided that between the further portion and the valve plate, an insulating material, preferably made of rubber or plastic, to further reduce the heat transfer from the compressed refrigerant to the valve plate.

The characterizing features of claim 7, namely the one-piece production of each component or the common one-piece production of the two pressure or suction channel forming components, in the latter case, the two together in one piece manufactured components touching at least along an intermediate wall, brings the Advantage of a simplified production. Thus, the component comprising the two channels can for example be injection molded from plastic, whereby the heat transfer from the pressure channel into the interior of the compressor housing, from the interior of the compressor housing in the suction channel and in the suction or pressure contact edge in the valve plate again reduced can be.

The characterizing features of claim 8 provide that the pressure bore occluding pressure valve is arranged in the pressure channel forming member. This allows the valve plate easier, ie. be manufactured in fewer steps, since the provision of a fastening for the pressure valve in the valve plate is no longer required. At the same time, the realization of this feature allows a pre-assembling of pressure channel and pressure valve or together with the features of claim 7, a pre-assembling of pressure channel and pressure valve, including suction channel.

According to the characterizing features of claims 9 and 10, namely the formation of a pressure chamber in the pressure channel immediately after the pressure bore pressure peaks in the pressure channel during expulsion of the refrigerant can be avoided from the cylinder, which would lead to a reduction in energy efficiency.

According to the characterizing features of claims 11,12 and 13, the attachment of the valve plate to the cylinder housing by means of a clamping element, which clamps the valve plate at least along a portion of its circumference, but preferably along the entire circumference against the cylinder housing. By this measure, the deformation and the cost of the cylinder shape over conventional cylinder heads of refrigerant compressors can be drastically reduced, since no screws for mounting the valve plate on the cylinder housing are more required.

The clamping element is latched according to the characterizing features of claim 14 with an end portion provided on the cylinder housing undercuts.

According to the characterizing features of claim 15 takes place with the other end portion which forms a first clamping leg, the clamping of the valve plate against the cylinder housing.

The cylinder housing is provided with a step according to the characterizing features of claim 16, in which the valve plate is at least partially recessed to allow a positioning thereof, as a positioning, as is known by screwing in conventional cylinder heads of refrigerant compressors, due to the clamping is no longer possible, with a preferred embodiment according to the characterizing features of claim 17 provides that the piston facing away from the surface of the valve plate is flush with the cylinder housing.

According to the characterizing features of claim 18, the fastening of the components forming the suction or pressure channel takes place on the valve plate by means of further clamping legs arranged on the clamping element. Thus, it is entirely possible to dispense with the use of screws for fastening the cylinder head.

Alternatively, it may be provided according to the characterizing feature of claim 19, that a separate further clamping element is provided, which clamps the suction or pressure channel forming components to the valve plate, said separate clamping element can be latched to the clamping element.

The characterizing features of claims 20 to 22 describe a further preferred embodiments of the invention, therefore, the valve plate by means of separate fasteners, such as screws, is attached to the cylinder housing, but the pressure or suction channel forming components are clamped to the valve plate, thus a combination of Clamping and screwing.

The characterizing features of claims 23 and 24 describe a preferred embodiment of the tight connection of the suction or pressure channel forming components to the valve plate in order to prevent leakage of the refrigerant from the channels into the interior of the compressor housing guaranteed can. The formation of the sealing bead in conjunction with the sealing projections requires a much lower required pressing force between printing or

Suction channel and valve plate as this is the case between cylinder cover and valve plate in known cylinder heads.

BRIEF DESCRIPTION OF THE FIGURES

Fig.1

eine axonometrische Ansicht einer Kolben-Zylinder-Einheit samt erfindungsgemäßem Zylinderkopf

Fig.2

eine Frontansicht eines erfindungsgemäßen Zylinderkopfes

Fig.3

eine axonometrische Ansicht einer Kolben-Zylinder-Einheit samt erfindungsgemäßem Zylinderkopf ohne Klemmelement

Fig.4

eine axonometrische geschnittene Detailansicht eines erfindungsgemäßen Zylinderkopfs

Fig.5

eine Sicht in Richtung Kurbelwellenachse auf einen Zylinderkopf samt Zylindergehäuse und Kurbelwellengehäuse

Fig.6

einen Schnitt entlang Linie AA aus Fig.2

Fig.7

eine Sicht in Richtung Kurbelwellenachse auf einen Zylinderkopf samt Zylindergehäuse und Kurbelwellengehäuse ohne Klemmelement

Fig.8

eine axonometrische Ansicht des den Druckkanal bildenden Bauteils

Fig.8a

eine axonometrische Ansicht des den Druckkanal bildenden Bauteils im Schnitt

Fig.9

eine alternative Ausführungsvariante eines erfindungsgemäßen Zylinderkopfes

Fig.10

eine Schnittansicht der alternativen Ausführungsvariante aus Fig.9 entlang der Ebene A1 aus Fig.9

Fig.11

eine Detailansicht aus Fig.10

Fig.12

eine Schnittansicht entlang der Ebene A aus Fig.9

Fig.13

eine weitere alternative Ausführungsvariante eines erfindungsgemäßen Zylinderkopfes

Fig.14

eine Schnittansicht entlang Ebene B aus Fig.13

Fig.15

eine zusätzliche alternative Ausführungsvariante eines erfindungsgemäßen Zylinderkopfes

Fig.16

eine Schnittansicht entlang Ebene C aus Fig.15

Fig.17

eine andere alternative Ausführungsvariante eines erfindungsgemäßen Zylinderkopfes

Fig.18

eine Schnittansicht entlang Ebene D aus Fig.17

Fig.19

eine Schnittansicht eines erfindungsgemäßen Zylinderkopfes mit O-Ringdichtung

Fig.20

eine Schnittansicht eines erfindungsgemäßen Zylinderkopfes mit Papierdichtung

Fig.21

eine Darstellung eines alternativen Dichtsystems im Schnitt entlang Ebene E aus Fig.22

Fig.22

eine zusätzliche, weitere Ausführungsvariante eines erfindungsgemäßen Zylinderkopfs gemäß Fig.21

Fig.23

eine Schnittansicht entlang Ebene F aus Fig.22

Fig.24-31

Schnittansichten eines alternativen Dichtungssystems

Fig.32

eine zusätzliche, alternative Ausführungsvariante eines erfindungsgemäßen Zylinderkopfes

Fig.33

eine Schnittansicht entlang Ebene G aus Fig.32

Fig.34

eine Draufsicht auf einen Zylinderkopf gem. Fig.32

Fig.35

eine Schnittansicht entlang Ebene H aus Fig.34

Fig.36

eine weiteres Ausführungsbeispiel eines erfindungsgemäßen Zylinderkopfes

Fig.37

eine axonometrische Ansicht des Zylindergehäuses samt Klemmelement gemäß Fig.36

Fig.38

eine weiteres Ausführungsbeispiel eines erfindungsgemäßen Zylinderkopfes

Fig.39

das Ausführungsbeispiel gemäß Fig.38 ohne den Druck- bzw. Saugkanal bildende Bauteile

Following is now a detailed description of the invention based on embodiments. Showing:

Fig.1

an axonometric view of a piston-cylinder unit including cylinder head according to the invention

Fig.2

a front view of a cylinder head according to the invention

Figure 3

an axonometric view of a piston-cylinder unit together with inventive cylinder head without clamping element

Figure 4

an axonometric sectional detail view of a cylinder head according to the invention

Figure 5

a view in the direction of the crankshaft axis on a cylinder head including the cylinder housing and the crankcase

Figure 6

a section along line AA Fig.2

Figure 7

a view in the direction of the crankshaft axis on a cylinder head including the cylinder housing and crankcase without clamping element

Figure 8

an axonometric view of the pressure channel forming member

Figure 8a

an axonometric view of the pressure channel forming member in section

Figure 9

an alternative embodiment of a cylinder head according to the invention

Figure 10

a sectional view of the alternative embodiment of Figure 9 along the A1 level Figure 9

Figure 11

a detailed view Figure 10

Figure 12

a sectional view taken along the plane A from Figure 9

Figure 13

a further alternative embodiment of a cylinder head according to the invention

Figure 14

a sectional view along plane B from Figure 13

Figure 15

an additional alternative embodiment of a cylinder head according to the invention

Figure 16

a sectional view along plane C from Figure 15

Figure 17

another alternative embodiment of a cylinder head according to the invention

Figure 18

a sectional view along plane D from Figure 17

Figure 19

a sectional view of a cylinder head according to the invention with O-ring seal

fig.20

a sectional view of a cylinder head according to the invention with paper seal

Figure 21

a representation of an alternative sealing system in section along plane E from Figure 22

Figure 22

an additional, further embodiment of a cylinder head according to the invention according to Figure 21

Figure 23

a sectional view along plane F from Figure 22

Fig.24-31

Sectional views of an alternative sealing system

fig.32

an additional, alternative embodiment of a cylinder head according to the invention

fig.33

a sectional view along plane G from fig.32

Fig.34

a plan view of a cylinder head gem. fig.32

Fig.35

a sectional view along plane H from Fig.34

Fig.36

a further embodiment of a cylinder head according to the invention

Fig.37

an axonometric view of the cylinder housing together with clamping element according to Fig.36

Fig.38

a further embodiment of a cylinder head according to the invention

Fig.39

the embodiment according to Fig.38 without the pressure or suction duct forming components

WAYS FOR CARRYING OUT THE INVENTION

Fig.1 shows an axonometric view of a cylinder head according to the invention, wherein portions of the cylinder housing 1, the valve plate 2, and the suction muffler 3 together with the intake opening 3a are visible.

The basic structure of the subject hermetically sealed refrigerant compressor is known per se. The piston-cylinder-motor unit consists essentially of a cylinder housing 1 and the therein a stroke advancing piston 4, and a crankshaft bearing 5 in a crankcase 5a, which is arranged perpendicular to the cylinder axis 6. The crankshaft bearing 5 receives a crankshaft (not shown) and protrudes into a central bore of the rotor Electric motor (also not drawn). The transmission of the rotational movement of the crankshaft to the piston 4 in a likewise known manner via a connecting rod (not shown). On the cylinder head itself, a suction muffler 3 is arranged to reduce the noise during the intake of the refrigerant to a minimum.

Fig.1 and Fig.2 show a variant of a cylinder head according to the invention in a fully assembled state, ie. with a clamping element 7, whereas Figure 3 the same cylinder head according to the invention, however, without clamping element 7 shows. Both components 8,9 are independent of each other and in particular also independent of the valve plate 2, with which, however, along a contact edge, namely a pressure contact edge 13 or a suction contact edge 17, which will be discussed in more detail later, are tightly connected. In other words, limit the components 8.9 which can also be referred to with pressure channel 8 and suction channel 9, each a completely self-sufficient channel, they completely encase until it hits the valve plate. According to the invention, the component 8 forming the pressure channel has a section 8a leading directly to the pressure bore 10 away from the valve plate 2 and a further section 8b adjoining this section 8a, which is essentially radially outward relative to the cylinder bore, preferably at a distance Z to the valve plate 2 is preferably parallel thereto (see also Figure 10 and 11 ).

The distance Z between the component 8 and the valve plate 2 causes optimum isolation of the valve plate 2 from the pressure channel, so that a heat transfer from the compressed, hot refrigerant in the pressure channel 8 on the valve plate 2 and on the suction channel 9 is strongly prevented.

Immediately following the arranged in the valve plate 2 pressure bore 10, for example, in Figure 4 it is evident in the Fig.1 and 2 However, is hidden, the component 8 forms a pressure chamber, which is arranged in the leading away from the valve plate 2 section 8a of the pressure channel 8 and a defined minimum volume does not fall below depending on the cooling capacity. This pressure chamber, which is also referred to in the following with 8a, serves to avoid possible pressure surges when expelling the refrigerant from the cylinder. The pressure channel 8 is then transferred to the further section 8b, which leads the refrigerant out of the compressor housing.

The components 8,9 become as outlined Fig.1 can be seen, pressed by a clamping element 7 against the valve plate 2. In the embodiment according to Fig.1 shown clamping element 7 is substantially Y-shaped and arched away from the piston 4 and is used exclusively for clamping the components 8,9 against the valve plate 2. The clamping element 7 itself is secured by screws 11 to the valve plate 2. The screws 11 are also used to attach the valve plate 2 to the cylinder housing. 1

Figure 4 shows the previously described cylinder head according to the invention with partially cut clamping element 7 and partially cut valve plate 2. The clamping element 7 presses with its one clamping portion 7a on a portion of the pressure channel forming member 8, whereby this against the valve plate 2 or more precisely via the pressure contact edge 13th pressed against the valve plate.

Figure 5 shows a view of the cylinder head according to the invention in the direction of the crankshaft axis. In this case, the structure of the cylinder head according to the invention can be seen very well, in particular the clamping element 7, the valve plate 2 and the cylinder housing 1, all of which are connected to each other via the screws 11.

Figure 6 shows a section along the line AA Fig.2 , In this case, the component 8 according to the invention can be seen very well, which forms the pressure channel and this completely encased. Also very clearly visible is the clamping element 7, which clamps the component 8 with its end portion 8c in the form of the pressure contact edge 13 against the valve plate 2 with its portion 7a. In this view, the distance Z can be seen very well, which is formed between the further portion 8b of the component 8 and the valve plate 2 and a heat transfer from the compressed, hot refrigerant-containing pressure channel 8 on the valve plate 2 and thus further into the cylinder interior 12th or in the suction channel 9, which is not visible in this sectional view, prevented. In contrast to conventional cylinder heads, the compressed refrigerant in the first section 8a of the pressure channel 8 is led away from the valve plate and then led away at a distance Z in the radial direction with respect to the cylinder bore from the cylinder housing 1 without the compressed refrigerant having further contact with the valve plate 2 ,

Figure 7 shows how Figure 5 a view of the cylinder head according to the invention in the direction of the crankshaft axis, but without clamping element 7, so that the pressure channel forming member 8 is very well visible, as well as the distance Z between the component 8 and the valve plate. 2

Fig.8 and Fig. 8a Both show that end portion of the portion 8a of the pressure channel forming member 8, which is sealed to the valve plate 2, which is not apparent in these figures, via the pressure contact edge 13. This, adjacent to the valve plate 2 and thus Connected end portion forms according to the invention a pressure chamber 8a to prevent pressure increases during expulsion of the refrigerant from the cylinder. The section 8a is further provided with receiving devices 19 in the form of pins, in which an end portion of a pressure valve 15 is suspended. The pressure valve 15 is formed in a conventional manner as a leaf spring element. That end section which can be suspended in the receiving devices serves as a fixed attachment section, whereas the free end section 15a opposite this end section alternately releases or closes the pressure bore 10 located immediately behind it in the valve plate 2 as a function of the compression cycle. The component 8 according to the invention is further provided with an opening limitation 26 in the form of a stop, as is apparent from Figure 8a is apparent. This opening limitation serves to limit the opening travel of the pressure valve 15.

The inventive arrangement of the pressure valve 15 in the component 8 allows the prefabrication of these two parts along a separate production line. Component 8 together with pressure valve 15 and opening limit 26 can then be easily and quickly connected by means of clamping element 7 with the valve plate 2. The conventional way of attaching the pressure valve 15 to the valve plate 2, for example by riveting is then no longer necessary, resulting in a significant simplification and, above all, acceleration of the manufacturing process.

Figure 9 shows an alternative embodiment of a cylinder head according to the invention, in which in addition to the pressure and suction passage forming components 8,9 and the valve plate 2 is fixed via a clamping element 7 with the clamping portions 7a and 7b on the cylinder housing 1. Thus, the comes in Figure 9 disclosed embodiment of a cylinder head according to the invention entirely without screws.

In other words, the entire cylinder head is merely clamped.

Figure 10 shows a sectional view of the alternative embodiment Figure 9 , wherein the heat transfer between the pressure channel 8 and valve plate 2 and between the suction channel 9 and valve plate 2 inhibiting distance Z is very clearly visible. The clamping element 7 consists in this case of a clamping portion 7b, which surrounds the valve plate 2 in its edge region over the entire circumference and snaps into this embodiment at an undercut 27 on the cylinder housing 1, as in the detail view in Figure 11 is clearly visible. Clearly visible in Figure 11 is also the dead space seal 14, which is arranged between the valve plate 2 and the cylinder housing 1, and the suction valve 32nd

The clamping element 7 has an additional clamping portion 7a, which is formed substantially U-shaped and the components 8,9 clamped against the valve plate 2.

Figure 12 shows a section along the plane A from Figure 9 , In this view, the integrality of the clamping element 7 with the clamping portions 7a and 7b can be seen very clearly. In addition, the transition of the pressure channel forming member 8 is shown in the pressure bore 10. The component 8 according to the invention is tightly connected to the valve plate 2 along the pressure contact edge 13. Within the enclosed by the pressure contact edge 13 surface is the pressure bore 10, and the movable part of the pressure valve 15. The area enclosed by the pressure contact edge 13 surface is also the only portion of the valve plate 2, which comes into contact with the compressed refrigerant from the cylinder.

Of course, the same also applies to the suction contact edge 17, along which the suction channel 9 tightly the valve plate 2 is connected. Within the area enclosed by the suction contact edge 17 is the suction bore 16. The area enclosed by the suction contact edge 17 is at the same time the only portion of the valve plate 2 which comes into contact with the refrigerant drawn into the cylinder.

The cylinder housing 1 has a shoulder 27, in which the valve plate 2 is at least partially, but preferably completely sunk, whereby at the same time a positioning of the valve plate 2 is achieved.

FIG. 13 and FIG. 14 both show a further alternative embodiment of a cylinder head according to the invention. However, the clamping element 7 is executed divided in the region of its clamping portion 7a, so that each component 8.9 has a clamping element 7 assigned to it.

Fig.15 and Fig.16 Both show an additional embodiment variant of a cylinder head according to the invention with an alternatively formed clamping element 7. The clamping portion 7b of the clamping element 7 surrounds the valve plate 2 in its edge region not over the entire circumference but is executed interrupted, the interruptions form openings in this clamping section, through which the components 8,9 away from the cylinder head and out to the cylinder head, so that actually several clamping portions 7b are present. However, the individual clamping portions 7b snap in the same manner as already described in the above-mentioned embodiments at an undercut 27 on the cylinder housing 1 a. The clamping portion 7a is formed cross-shaped in this embodiment, each one arm of this cross merges into a clamping portion 7b. The area where the individual arms of the cross meet is included made cylindrical and causes the clamping of the components 8.9.

Fig.17 and Fig.18 show another alternative embodiment of a cylinder head according to the invention, in which the clamping element 7, both the components 8,9 and the valve plate 2 clamped against the cylinder housing 1. In this case, however, the cylinder housing 1 is formed laterally raised, wherein the raised portion 1a has an undercut, in which the clamping element 7 with its clamping portion 7b can be latched. The valve plate 2, which terminates the cylinder housing 1 at the end and is axially surmounted by its portions 1a, is clamped in this case by the clamping portions 7b, which are latched to the undercut of the portion 1a, against the cylinder housing 1. The clamping portion 7a, which in turn integrally forms with the clamping portion 7b, the clamping element 7, clamps the components 8,9 against the valve plate 2. The raised portion 1a is provided with openings 18 through which the components 8,9 away from the cylinder head or to Cylinder head are led out.

The Fig.19 and 20 each show a sectional view of cylinder heads according to the invention, in which on the one hand an O-ring seal 20 and on the other hand, a paper seal 21 for sealing the connection of the suction channel 9 and also the pressure channel 8 with the valve plate 2 are used. This type of seal is already known from the prior art, but there is the sealing of the connection of the valve plate with the cylinder cover, which is no longer necessary in a cylinder head according to the invention.

Figure 21 shows an alternative embodiment of a possible sealing of the connection of the pressure channel 8 and the suction channel 9 with the valve plate 2 based on an additional, further embodiment of an inventive Cylinder head. As a sealing system is provided here, the valve plate 2 to be provided with a sealing bead 23, in which a the contour of the sealing bead 23 on the valve plate 2 substantially corresponding to the Druckkontaktante 13 of the pressure channel forming member 8 and at the Saugkontaktkante 17 of the Suction passage forming component 9 9 arranged sealing extension 22 (see also 8 and 8a ) intervenes.

Of course, a reverse embodiment is conceivable, ie. at the pressure contact edge 13 of the pressure channel forming member 8 and at the Saugkontaktkante 17 of the suction channel forming member 9 (see also 8 and 8a ), a sealing bead 23 is provided, in which a corresponding to the contour of the sealing bead 23, arranged on the valve plate 2 sealing projection 22 engages.

In order to ensure a sealing of the connection, the sealing extension 22 must either have a larger volume than the sealing bead 23 or the shape of the sealing extension 22 is different from that of the sealing bead 23. The applied during assembly of the cylinder head pressing forces, in particular the clamping forces of the clamping element 7 then cause the flow of the sealing extension 22 in the sealing bead 23 or of parts of the sealing extension 22 due to the high local surface pressure.

The formation of the sealing bead 23 in conjunction with the sealing projections 22 requires for the same tightness a much lower required pressing force between the pressure or suction passage 8.9 and valve plate 2 than is the case between cylinder cover and valve plate 2 in known cylinder heads. Although the surface pressure required is the same for both systems, the sealing surfaces are quite different, namely a long wide seal in the case of the paper seal and a short narrow one Sealing surface in the case of the sealing bead 23 - sealing extension 22 system.

The sealing system works independently of the material pairings used. So conventional material pairings are possible, such as metal (valve plate 2) - metal (components 8,9) or metal (valve plate 2) - flowable plastic (components 8,9) or plastic (valve plate 2) - flowable plastic (components 8 , 9).

The surface pressure required for the present application can be given as 5 to 20 N / mm ² . A particularly preferred geometric shape of the sealing bead 23 is the V-shape or U-shape according to FIGS Fig.24 to 31 , those of the sealing extension 23, the pin shape, wherein the free end of the sealing extension is preferably flattened or rounded.

Figure 24 shows a simple embodiment of the sealing system with V-shaped sealing bead 23 and pin-shaped sealing extension 22nd

Figure 25 shows a sealing bead 23 formed by two projecting from the valve plate 2 ribs, which cooperates with a pin-shaped sealing extension 22.

In both cases, the peg-shaped sealing extension 22 is flattened at its free end.

In Figure 26 two peg-shaped sealing projections 22 are provided on the pressure channel 8, which limit a V-shaped sealing bead 23, in which engages a arranged on the valve plate 2 pin-shaped sealing extension 22. In addition, sealing beads 23 are arranged on the valve plate 2, in which the two arranged on the pressure channel 8 sealing projections 22 engage, so that a kind of toothing between the pressure channel or suction channel forming components 8,9 and the valve plate 2 comes. The cone-shaped sealing projections 22 are provided at their free end region with a chamfer.

Fig.27 to 31 show developments of the sealing system just described, wherein the peg-shaped sealing projections 22 are executed rounded at its free end.

The sealing system according to the invention can be used both in the cylinder heads described in this application according to the invention as well as in cylinder heads according to the prior art, ie using cylinder covers. In the latter case, the cylinder cover the sealing extension 22 and the sealing bead 23 and the valve plate 2, the corresponding counterpart.

The Figure 22 and 23 show further views of the additional, further embodiment of the cylinder head according to the invention Figure 21 ,

The FIGS. 32 to 35 show an additional alternative embodiment of a cylinder head according to the invention with the components 8.9. The valve plate 2 is, with the exception of the suction or pressure bore 16.10 coated with a plastic jacket 25 which faces away from the cylinder housing 1 and a cylinder housing facing portion. Those components forming the pressure or suction channel 8, 9 are integrated into the plastic layer 25, ie. are also made of plastic.

The production takes place in this case in several steps.

First, the valve plate 2 with plastic 25 overmolded (insert technology), wherein on the side facing away from the cylinder housing 1 side of the valve plate 2 already pins 28, which serve for positional positioning of the pressure valve 15 (according to the receiving devices 19), be sprayed with.

At the piston 4 zugewanden side is overmolded plan. Here no holding devices for the suction valve are needed. It is merely an exemption to provide for the position positioning of the suction valve. The suction valve itself is clamped between the end face of the cylinder housing 1 and the valve plate 2.

In a further step, in order to connect the pressure channel-forming component 8 and the suction channel-forming component 9, which are also made of plastic in a separate step, with the valve plate 2, along the sealing beads 24, in their outline of the pressure contact edge 13 and suction contact edge 17 correspond and are not arranged in this embodiment in the valve plate 2, but in the valve plate 2 surrounding plastic jacket 25, made a laser welding or vibration welding of the plastic parts.

The attachment of the valve plate 2 on the cylinder housing 1 by means of clamping element 7, as already in the previous embodiments.

Fig.36 and 37th show a variant of a cylinder head, in which in addition to the clamping element 7, a further clamping element 29 is provided. This is according to the invention attached to the clamping element 7 and locked with this. On the valve plate 2 in this case, a pressure valve 15 forming, plate-shaped element 30, preferably made of metal, is provided, which is clamped by the clamping element 7 to the valve plate 2. The opening limit 26 for the pressure valve 15, as already in Figure 21 or 35 shown, integrated in the component 8.

The components 8,9 are made in this case as a one-piece plastic part.

In the in Fig.38 In the embodiment shown, the components 8, 9 are adhesively bonded to the valve plate 2, the pressure valve 15 in this case being arranged in the component 8, as already described above.

Fig.39 shows the orientation of the pressure valve 15, as a leaf spring, relative to the valve plate 2, wherein the components 8.9 have been omitted to illustrate the readability of the drawing.

LIST OF REFERENCE NUMBERS

1.

cylinder housing

1a.

raised portion of the cylinder housing

Second

valve plate

Third

suction silencer

3a.

suction

4th

piston

5th

crankshaft bearings

5a.

crankcase

6th

cylinder axis

7th

clamping element

7a.

clamping section

7b.

clamping section

8th.

the pressure channel forming component

8a.

wegführender section of the pressure channel, pressure chamber

8b.

another section of the pressure channel

9th

the suction channel forming component

10th

pressure bore

11th

screw

12th

Cylinder interior

13th

Pressure contact edge

14th

Dead space seal

15th

pressure valve

15a.

free end portion of the pressure valve

16th

suction bore

17th

Saugkontaktkante

18th

breakthroughs

19th

cradles

20th

O-ring seal

21st

paper gasket

22nd

Sealing projection

23rd

sealing bead

24th

sealing bead

25th

Plastic sheath

26th

Cushioned limit

27th

undercut

28th

pins

29th

another clamping element

30th

plate-shaped element

31st

paragraph

32nd

suction

Claims (24)

1. A hermetically encapsulated refrigerant compressor having a hermetically sealed compressor housing, in whose interior a piston-cylinder unit, which compresses a refrigerant, operates, whose cylinder housing (1) is closed using a valve plate (2) having a pressure hole (10) and a suction hole (16), and a suction channel and a pressure channel are provided, via which refrigerant is suctioned via a suction valve (32) into the suction hole (16) and is compressed via a pressure valve (15) from the pressure hole (10) in the pressure channel, the suction channel being formed by a channel-shaped component (9) which connects the suction hole (16) to a preferably provided suction noise damper (3), characterized in that the pressure channel is formed by an independent component (8) completely enveloping the pressure channel, which is tightly connected to the valve plate (2) along a pressure contact edge (13) formed by an end section of the component (8), the pressure hole (10) and the mobile part of the pressure valve (15) being situated inside the area enclosed by the pressure contact edge (13).
2. The hermetically encapsulated refrigerant compressor according to Claim 1, characterized in that the ratio of the cross-sectional area of the pressure hole (10) to the area enclosed by the pressure contact edge (13) is greater than 1/12.
3. The hermetically encapsulated refrigerant compressor according to Claim 1 or 2, characterized in that the area enclosed by the pressure contact edge (13) exceeds the area of the mobile parts of the pressure valve by less than 50%.
4. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 3, characterized in that the component (8) forming the pressure channel has a section (8a) directly adjoining the pressure hole (10) and leading away from the valve plate (2), and a further section (8b) adjoining this section (8a), which runs radially outward in relation to the cylinder hole, preferably at a distance to the valve plate (2) and preferably parallel thereto.
5. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 4, characterized in that the section (8a) leading away from the valve plate (2) and/or the further section (8b) of the pressure channel (8) is/are manufactured from plastic.
6. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 5, characterized in that an insulating material, preferably made of rubber or plastic, is situated between the further section (8b) and the valve plate (2).
7. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 6, characterized in that the component (8) forming the pressure channel and the component (9) forming the suction channel are each manufactured in one piece and/or are preferably manufactured jointly in one piece, the two components (8, 9) manufactured jointly in one piece preferably being in contact along an intermediate wall, but at least along connecting webs.
8. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 6, characterized in that the pressure valve (15) closing the pressure hole (10) is fastened in the component (8) forming the pressure channel.
9. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 7, characterized in that a pressure chamber (8a), which does not fall below a predefined minimum volume, is provided in the component (8) forming the pressure channel.
10. The hermetically encapsulated refrigerant compressor according to Claim 9, characterized in that the pressure chamber (8a) is situated directly adjoining the pressure hole (10) in the component (8) forming the pressure channel.
11. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 10, characterized in that a clamping element (7) is provided, which clamps the valve plate (2) to the cylinder housing (1) along at least a section of its circumference, but preferably along the entire circumference.
12. The hermetically encapsulated refrigerant compressor according to Claim 11, characterized in that the clamping element (18) has an essentially J-shaped cross-section.
13. The hermetically encapsulated refrigerant compressor according to Claim 11 or 12, characterized in that the clamping element (7) is implemented as circular.
14. The hermetically encapsulated refrigerant compressor according to one of Claims 11 through 13, characterized in that one or more undercuts (27), which may be engaged with an end section of the clamping element (7), are provided on the cylinder housing (1).
15. The hermetically encapsulated refrigerant compressor according to one of Claims 11 through 14, characterized in that the other end section of the clamping element (7) forms a first clamping section (7b), which clamps the valve plate (2) to the cylinder housing (1).
16. The hermetically encapsulated refrigerant compressor according to one of Claims 11 through 15, characterized in that the cylinder housing has a shoulder (31), in which the valve plate (2) is at least partially countersunk.
17. The hermetically encapsulated refrigerant compressor according to one of Claims 11 through 16, characterized in that the surface of the valve plate (2) facing away from the piston (4) terminates flush with the cylinder housing (1).
18. The hermetically encapsulated refrigerant compressor according to one of Claims 11 through 17, characterized in that the clamping element (7) has at least one further clamping section (7a), which clamps the components (8, 9) forming the pressure channel and the suction channel to the valve plate (2) or in the suction hole (16) and/or the pressure hole (10).
19. The hermetically encapsulated refrigerant compressor according to one of Claims 11 through 17, characterized in that a further clamping element (29) is provided, which may be engaged on the clamping element (7) and clamps the components (8, 9) forming the pressure channel and the suction channel to the valve plate (2) or in the suction hole (16) and/or the pressure hole (10).
20. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 10, characterized in that separate fasteners (11) are provided and/or a separate fastener (7b) is provided for fastening the valve plate (2) to the cylinder housing (1).
21. The hermetically encapsulated refrigerant compressor according to Claim 20, characterized in that the separate fasteners are screws (11).
22. The hermetically encapsulated refrigerant compressor according to one of Claims 20 or 21, characterized in that a clamping element is provided, which may be engaged on the cylinder housing (3) and clamps the components (8, 9) forming the pressure channel respectively the suction channel to the valve plate (2) or in the suction hole (16) and/or the pressure hole (10).
23. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 22, characterized in that preferably V-shaped sealing beads (23) are provided in the valve plate (2), and the front face, facing toward the valve plate (2), of the components (8, 9) forming the suction channel and the pressure channel is equipped along its suction or pressure contact edge (13, 17) with sealing projections (22) essentially corresponding to the V-shaped sealing beads (23), the sealing projections (22) being implemented as different in their geometrical design from the sealing beads (23) and/or having a different volume.
24. The hermetically encapsulated refrigerant compressor according to one of Claims 1 through 22, characterized in that sealing projections (22) are provided in the valve plate (2), and the front face, facing toward the valve plate (2) of the components (8, 9) forming the suction channel and the pressure channel is equipped along its suction or pressure contact edge (13, 17) with sealing beads (23) essentially corresponding to the sealing projections (22), the sealing projections (22) being implemented as different in their geometrical design from sealing beads (23) and/or having a different volume.

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