EP1563189A1

EP1563189A1 - Helical compressor for refrigerating medium

Info

Publication number: EP1563189A1
Application number: EP03808684A
Authority: EP
Inventors: Karl-Friedrich Kammhoff; Thomas Varga
Original assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Current assignee: Bitzer Kuehlmaschinenbau GmbH and Co KG
Priority date: 2002-10-15
Filing date: 2003-08-20
Publication date: 2005-08-17
Anticipated expiration: 2023-08-20
Also published as: CN1688817B; WO2004036044A1; EP1413758A2; EP1563189B1; US20040126261A1; CN102116293B; EP2511531A3; US20050232800A1; EP1413758B1; DE10248926A1; DE50302045D1; CN102116293A; EP2511531B1; US7112046B2; SI1413758T1; CN1688817A; CN1497182A; DK1413758T3; EP1413758A3; US6960070B2

Abstract

The invention relates to a compressor for refrigerating medium, comprising: an outer housing (10); a helical compressor (12) that is placed inside the outer housing (10); an outlet (36), which is located in the bottom (20) of the stationary compressor body (16) and which leads to a high pressure chamber (210) in the outer housing (10), and; a check valve (208), which has a valve body (220) and which is placed between the outlet (36) and the high pressure chamber (210). The aim of the invention is to improve a compressor of the aforementioned type in order to guarantee the most optimal possible functioning of the check valve (208). To this end, the invention provides that the outlet (36) has a central axis (222) that is offset with regard to a central axis (224) of the valve seat (218) for the valve body (220) in a transverse direction to center axis (224).

Description

SPIRAL COMPRESSOR FOR REFRIGERANT

The invention relates to a compressor for refrigerants, comprising an outer casing, a arranged in the outer casing scroll compressor with a first, fixedly arranged in the outer casing compressor body and a second, relative to the first compressor body movable compressor body, each having a bottom and above the respective soil rising first or comprise second scroll ribs, which so into one another - _'engage that for compressing the refrigerant, the second compressor body opposite the first compressor body to form chambers on an orbital path about a central axis is movable, a leading to a high pressure chamber in the outer housing outlet in the bottom of the fixed compressor body and arranged between the outlet and the high-pressure chamber check valve with a valve body, which in a between a valve seat and a Hubfänger extending movement space freely between a through the Valve seat fixed closing position and an established by the Hubfänger open position is movable.

Such a compressor with a check valve is known from US 5,451,148.

In such a check valve is generally the requirement that this opens quickly, closes quickly and when opening as quickly as possible the largest possible cross-sectional area for a flow available. Invention is therefore an object of the invention to improve a compressor of the type described above in that the best possible function of the check valve is guaranteed.

This object is achieved in a compressor of the type described above according to the invention in that the outlet has a central axis which is offset from a central axis of the valve seat for the valve body in a transverse direction to the central axis. This solution has the advantage that by the staggered arrangement of the outlet relative to the valve seat, the valve when opening undergoes an asymmetric force by the inflowing refrigerant and thus opens quickly.

Particularly advantageously, the rapid opening of the valve body can be achieved when a cross-sectional area of a passage opening of the valve seat is greater than a cross-sectional area of the outlet, so that a relatively large force can be generated on the valve body by the impinging on the valve body refrigerant.

In order to perform the passage opening with a cross-sectional area which is larger than the cross-sectional area of the outlet, it is preferably provided that between the valve seat and the outlet a larger cross-sectional area than the outlet having prechamber is arranged.

This prechamber expediently has a cross-sectional area which corresponds either to the cross-sectional area of the passage opening, which in turn should be larger than the cross-sectional area of the outlet, or larger than the cross-sectional area of the passage opening of the valve seat. With regard to the arrangement of the prechamber relative to the outlet is advantageously provided that a central axis of the prechamber is arranged offset transversely to the central axis of the outlet.

It is particularly favorable if the center axis of the pre-chamber coincides substantially with the center axis of the valve seat and thus both are arranged substantially coaxially with one another.

For receiving and guiding the valve body, preferably the movement space between the valve seat and the Hubfänger is provided.

In order to be able to use a valve body with the smallest possible mass at the largest possible opening through the valve seat, it is preferably provided that the movement space extends from the valve seat to the Hubfänger with an approximately the valve seat, ie in particular an outer diameter thereof, corresponding cross-sectional area in the direction of its central axis ,

Furthermore, there is an advantageous force acting on the valve body when opening and keeping open the check valve when the center axis of the movement space coincides substantially with the central axis of the valve seat.

With regard to the valve body so far no further statements have been made. Thus, valve bodies with a central plate-shaped part are known from the prior art, from which further arms extend or which is enclosed by openings. A structurally optimal solution provides that the valve body is plate-shaped with an approximately corresponding to the valve seat outer contour. This solution has the advantage that no unnecessary the mass of the valve body enlarging additional arms or other elements are necessary to guide the valve body. On the contrary, such a valve body can be optimally held and guided in the movement space defined above, whose cross-sectional area approximately corresponds to the cross-sectional area of the valve seat.

In particular, in a plate-shaped valve body whose outer contour corresponds approximately to the valve seat, there is the problem that in the open position of the valve body, the entering into the movement space via the passage opening of the valve seat refrigerant must be led out of the movement space.

Preferably, it is provided for this purpose that at least one outlet space is arranged laterally of the movement space, in particular radially outside thereof, which opens laterally into the movement space with an outlet opening between the lift catcher and the valve seat and leads to an outlet opening.

Such an outlet space makes it possible, when the valve body is lifted off from the valve seat, in particular in the open position, to allow the refrigerant flow which propagates in the direction of the pressure arm to emerge with as large a cross-section as possible and unhindered into the high-pressure chamber. A particularly large cross-section for the mouth opening the outlet space into the movement space is available when the outlet opening of the outlet chamber extends to the valve seat, preferably between the Hubfänger and the valve seat.

The outlet opening of the outlet space could, for example, be arranged opposite the outlet opening. A structurally expedient solution provides that the outlet opening is arranged in the region of the Hubfängers.

Preferably, the outlet opening is arranged so that it merges into a passage opening in the Hubfänger and thus the exiting refrigerant flow through the outlet and the outlet opening also passes through the Hubfänger.

In order to have optimum flow cross sections available, it is preferably provided that a plurality of outlet spaces are arranged around the movement space.

With regard to the limitation of the movement space, no further details have been given so far. Thus, an advantageous solution provides that the movement space is limited by at least one adjacent to the at least one mouth opening wall surface.

Preferably, such a wall surface serves as a guide surface for the valve body, so that it is always held in the space provided for movement. It is particularly advantageous if the valve body is guided by a plurality of equally spaced around the central axis of the movement space arranged guide surfaces.

In principle, there would be the possibility of intercepting the valve body by multiple contact points on the Hubfänger. However, this has the disadvantage that so that the valve body must be made very stable when no damage to the valve body when intercepting the same should occur on the Hubfänger, since when starting the compressor, the valve body at high speed moves in the direction of the Hubfängers and then intercepted by this becomes.

Preferably, for this purpose, the valve body is provided with an end face which can be applied areally to the contact surface of the valve body.

With regard to the sizes of the contact surface and the face, no further details have been given so far.

Thus, it is preferably provided that the contact surface has a surface area which is greater than half the surface area of the end surface.

It is even better if the contact surface has a surface area which corresponds approximately to the surface area of the end face.

Even with regard to the formation of the face itself so far no details have been made. Thus, it is preferably provided that the valve body is plate-shaped and the end face has a surface area which corresponds to more than half of an extension of the valve body transversely to its central axis. Preferably, the surface area of the end face is so large that it substantially corresponds to the cross-sectional area of the valve body.

In order to prevent the valve body from adhering to the Hubfänger by adhesion at falling pressure in the scroll compressor and does not change fast enough into the closed position, it is preferably provided that the Hubfänger is provided with an opening which extends from a lying in the contact surface orifice extends to a high pressure side of the lift catcher. This ensures that the check valve closes quickly at a pressure drop in the scroll compressor, since even in the event that the valve body should stick to the Hubfänger, the valve body quickly dissolves the Hubfänger due to the pressurization of the breakthrough.

Particularly quickly, the valve body can be released from Hubfänger when the breakthrough is located laterally of the central axis of the movement space and thus causes the first acting on the valve body over the breakthrough force tilting of the valve body.

Conveniently, the aperture is disposed in an angular segment located on an opposite side of the central axis of the movement space from the central axis of the outlet, so that the aperture lies in a semicircle about the central axis of the movement space, while the central axis of the outlet is in the other semicircle.

Preferably, the angular segment in which the aperture is located is symmetrical to a plane passing through the central axis of the outlet and the central axis of the movement space. The angle segment could comprise a whole semicircle.

However, it is particularly advantageous if the angular segment within which the at least one breakthrough lies is approximately 150 °, more preferably approximately 120 °.

With regard to the arrangement of the passage openings in Hubfänger no detailed information has been made so far. In order not to limit the available for the refrigerant flow cross-sectional area, it is preferably provided that the passage openings are in the Hubfänger outside of the movement space final part of the Hubfängers same.

Further features and advantages are the subject of the following description and the drawings of some embodiments.

In the drawing show:

1 shows a longitudinal section through an embodiment of a compressor according to the invention.

Figure 2 is a rotated by an angle of approximately 90 ° longitudinal section through the embodiment of the compressor according to the invention.

Fig. 3 is a section along line 3-3 in Fig. 1;

Fig. 4 is a section along line 4-4 in Fig. 1; Fig. 5 is a plan view of a bottom of a motor housing forming bearing part;

Fig. 6 is a perspective view of a section in the region of a check valve;

Fig. 7 is an enlarged sectional view similar to Figure 1 in the region of the check valve.

Fig. 8 is a section along line 8-8 in Fig. 7;

Fig. 9 is a section along line 9-9 in Fig. 7;

10 shows a section corresponding to FIG. 7 with the valve body in the open position; FIG.

11 is a section along line 11-11 in Fig. 7th

An embodiment of a compressor according to the invention, shown in Fig. 1 to 5, comprises a designated as a whole with 10 outer housing in which a designated as a whole by 12 scroll compressor is arranged, which is drivable by a designated as a whole by 14 drive unit.

The scroll compressor 12 comprises a first compressor body 16 and a second compressor body 18, wherein the first compressor body 16 has a same raised above a bottom 20 of the first, in the form of a circular involute spiral rib 22 and the second compressor body 18th a rising above a bottom 24 of the same, in the form of a circular involute spiral rib 26, wherein the spiral ribs 22, 26 engage each other and sealingly abut each of the bottom surfaces 28 and 30 of the other compressor body 18, 16, so that between The spiral ribs 22, 26 and the bottom surfaces 28, 30 of the compressor body 16, 18 chambers 32 form, in which a compression of a refrigerant takes place, which flows over a spiral ribs 22, 26 radially surrounding the outside suction 34 with initial pressure and after compression in the Chambers 28 via an outlet 36, provided in the bottom 20 of the first compressor body 16, compressed to high pressure exits.

In the described first embodiment, the first compressor body 16 is held firmly in the outer housing 10, by means of a separating body 40, which in turn is held on the outer housing 10 within the same, the bottom 20 of the first compressor body 16 overlaps at a distance and tight with a around the outlet 36 extending around annular flange 42 of the first compressor body 16, which projects beyond the bottom 20 on one of the spiral rib 26 opposite side is connected.

Thus, a cooling chamber 44 for cooling the bottom 20 of the first compressor body 16 is formed between the bottom 20 of the first compressor body 16 and the separator body 40, which is for example the subject of WO 02/052205 A2, to which reference is made in full with respect to the cooling of the scroll compressor 12 becomes.

In contrast to the first compressor body 16, the second compressor body 18 is movable about a central axis 46 on an orbital path relative to the first compressor body 16, the spiral ribs 22 and 26 theoretically along a contact line abut each other and the contact line also rotates during the movement of the second compressor body 18 on the orbital path about the central axis 46.

The drive of the second compressor body 18 on the orbital path about the central axis 46 is effected by the already mentioned drive unit 14 which comprises an eccentric drive 50, a drive shaft 52 driving the eccentric drive 50, a drive motor 54 and a bearing unit 56 for supporting the drive shaft 52.

In detail, the eccentric drive 50 is formed by an eccentrically arranged on the drive shaft 52 and thus eccentrically to the central axis 46 driver 62 which engages in a fixedly connected to the bottom 24 of the second compressor body 18 driver receptacle 64, thus the second compressor body 18 on the orbital path to move about the central axis 46.

The bearing unit 56 in turn comprises a first bearing body 66, which constitutes a main bearing body and with a bearing portion 68, the drive shaft 52 in a region 70 supports and which carries the driver 62, wherein the driver 62 is preferably arranged integrally with the region 70.

Furthermore, the first bearing body 66 encloses a space 72 in which the eccentric drive 50 is arranged and in which a balancing mass 74 fixedly connected to the drive shaft 52 moves. In addition, the first bearing body 66 extends laterally of the space 72 in the direction of the bottom 24 of the second compressor body 18 and has around a second compressor body 18 facing opening 76 of the space 72 around extending wings 78, on which the second compressor body 18 with a the second spiral rib 26 rests opposite rear side 80 and is thus supported so that the second compressor body 18 is thereby secured against movement away from the first compressor body 16.

The fixation of the first bearing body 66 in the outer housing 10 is carried out with retaining arms 82 which extend radially from the first bearing body 66 to the outer housing 10 and hold in this the first bearing body 66 precise.

The first bearing body 66 further has on an opposite side of the holding arms 82 an outer surface 84 on which a within and spaced from a cylindrical portion 86 of the outer housing 10 extending, preferably also cylindrical housing sleeve 88 of a motor housing 90 sits, up to a second bearing body 92 forming a bottom of the motor housing 90, which is arranged at a distance from the first bearing body 66 and forms a bearing portion 94, in which the drive shaft 52 is mounted with an end portion 96 coaxial with the central axis 46.

For additional stabilization of the second bearing body 92 is still supported by support body 98 on the outer housing 10. The entire motor housing 90 thus extends within the cylindrical portion 86 of the outer housing 10 and at a distance therefrom.

In the motor housing 90, the drive motor 54 is disposed between the first bearing body 66 and the second bearing body 92, which comprises a rotor 100 seated on the drive shaft 52 and a rotor 102 surrounding the stator 102, wherein the stator 102 of the housing sleeve 88 of the motor housing 90th is held stably fixed relative to the outer housing 10, so that a conventional gap 104 between the rotor 100 and the stator 102 is made.

In addition, the stator 102 is provided on its housing sleeve 88 side facing with cooling channels 106 which extend parallel to the central axis 46, for example in the form of outer grooves in the stator 102 over the entire plant side 108, wherein the stator 102 via the plant side 108 at the housing sleeve 88 is supported.

Between the second bearing body 92 and a bottom portion 110 of the outer housing 10, a free space 112 is provided, which opens up the possibility that at about the bottom portion 110 with approximately vertically extending central axis 46 uplifting outer housing 10 forms an oil sump 114, in which on the one hand lubricating oil due to gravity collects and on the other hand lubricating oil for lubricating the compressor according to the invention is kept ready.

Into the oil sump 114, an oil delivery pipe 116 extending from the end region 96 of the drive shaft 52 and extending coaxially therewith, which has a delivery vane 120 in its interior 118, and thus acts as an oil pump, which pumps oil from the oil sump 114 in a drive shaft 52 passing through the lubricating oil passage 122, which leaves a mouth opening 124 lubricating oil on an end face 126 of the driver 62 to a formed between the cam receiver 64 and the driver 62 pivot bearing for the To lubricate movement of the second compressor body 18 on the orbital track.

Furthermore, branches from the lubricating oil passage 122 from a transverse channel 128, which leads to the formed between the bearing portion 68 of the first bearing body 66 and the portion 70 of the drive shaft 52 pivot bearing and this lubricates and finally branches off from the lubricating oil passage 122 from a vent passage 130.

The oil used to lubricate the driver 62 in the driver seat 64 leaves the driver seat 64 in the region of an opening 132 of the driver seat 64 facing the area 70, then passes to a floor 134 of the room 70 formed by the first bearing body 66 and from there Drain channels 136, which form an oil guide with the bottom 134, in an upper interior 140 of the motor housing 90. Further, the oil that serves to lubricate the portion 70 of the drive shaft 52 in the bearing portion 68, on an underside 142 of the bearing portion 68 thereof and thus also in the upper interior 140 of the motor housing 90 a.

The supply of to be compressed by the scroll compressor 12 refrigerant to the compressor according to the invention via a suction line 150, which is guided to a suction port 152, which in turn is held on the outer housing 10, but is guided through this to the motor housing 90. Preferably, the suction port 152 has a sleeve 154, which passes through the outer housing 10 of the compressor according to the invention and engages in a fixedly connected to the housing sleeve 88 of the motor housing 90 receptacle 156, as shown in Fig. 1 and 3. The receptacle 156 encloses an opening provided in the housing sleeve 88 inlet 158 for the refrigerant, so that it can enter directly into a lower interior 160 of the motor housing 90, which is located between the stator 102 and the second bearing body 92.

Further, the inlet opening 158 is arranged in the direction of the central axis 46 so that the refrigerant enters at the level of a winding head 162 of the stator 102 in the lower interior 160, which also protrudes into the inner space 160.

For optimal distribution of the refrigerant in the lower interior 160 of the inlet 158 is associated with a deflection unit 164 which has two deflection surfaces 166 and 168, which deflect the approximately in the radial direction 170 to the central axis 46 by the sleeve 154 incoming refrigerant so that the main flow directions of the supplied gaseous refrigerant in two opposite azimuthal directions 172 and 174 to the central axis 46 around the winding head 162 around and within the housing sleeve 88, the inner wall 176 continues to propagate in the azimuth directions 172 and 174 refrigerant and contributes to that with the supplied refrigerant entrained oil is deposited on the inner wall 176 and runs at this in the direction of the in Fig. 5 individually shown second bearing body 92 down. Wherein the bearing body 92 and the Housing sleeve 88 substantially occlusive bottom 178 forms, however, which is provided with oil drain holes 180, from which the separating oil can flow into the oil sump 114.

Due to the closed bottom 178, the refrigerant entering the lower inner space 160 of the motor housing 90 is substantially incapable of transferring into the free space 112 between the second bearing body 92 and the base 110, but remains substantially in the inner space 160 for cooling the Winding head 162 and then exits from the inner space 160 through the cooling channels 106 and the gap 104 between the rotor 100 and the stator 102 in the upper inner space 140 which lies between the first bearing body 66 and the stator 102 to those in the upper interior 140 projecting winding heads 182 to cool.

At the level of the winding head 82 is in the housing sleeve 88, as shown in FIGS. 1 and 4, at least one outlet opening 184 is provided, through which the refrigerant from the upper interior 140 of the motor housing 90 exits, in a gap 188 which between the cylindrical portion 88 and the first bearing body 66 except for the retaining arms 82 and the motor housing 90, and which part of an oil separator 190 is. In particular, the gap 188 is located substantially between an inner wall surface 192 of the cylindrical portion 86 of the outer housing 10 and an outer wall surface 194 of the cylindrical housing sleeve 88, wherein the gap 188 preferably extends as a closed annular space around the housing sleeve 88 around. In order to generate a flow of the gaseous refrigerant in oppositely extending azimuthal directions 196, 198 in the intermediate space 188, a deflection unit 200 is arranged opposite the outlet opening 184, which has deflection surfaces 202 and 204 which direct the gaseous refrigerant emerging from the outlet opening 184 in the azimuthal directions Divert 196 and 198.

However, it is also conceivable to provide a plurality of outlet openings 184 opening into the intermediate space 188 and deflecting units 200 associated therewith at an angular distance around the central axis 46.

By guiding the gaseous refrigerant in the azimuthal directions 196 and 198, in particular between the inner wall surface 192 and the outer wall surface 194, due to the ever-acting radial acceleration of oil droplets in the gaseous refrigerant, an oil separation effect occurs, which occurs particularly in a precipitate oil carried by the refrigerant on the inner wall surface 192 and the outer wall surface 194, the oil with the compressor mounted substantially vertical center axis 46 between the outer housing 10 and the motor housing 90 preferably along the inner wall surfaces 192 and the outer wall surface 194 in the direction of the oil sump 114 may occur because between the outer housing 10 and the motor housing 90 over the entire extent of the motor housing 90 in the direction of the central axis 46, starting from the gap 188 in the free space 112 overflowing free space 206 consists of wel chen the oil is ultimately fed to the oil sump 114. In the oil separator 190, the deposition of all, from the refrigerant on its way through the inner space 160, through the gap 104 and the cooling channels 106 and the interior 140 entrained oil, in particular at least partially oil, which exits at the bottom 142 of the bearing portion 68 , and oil that has been supplied to the interior space 140 via the drainage channels 136.

The refrigerant thus substantially freed of oil in the oil separator 190 then flows, starting from the space 188 of the oil separator 190, between the holding arms 82 and thus outwardly past the first bearing body 66 in the direction of the suction region 34 of the spiral compressor 12 and is sucked and compacted by the latter. wherein the compressed refrigerant through the outlet 36 and a subsequent check valve 208 enters a high-pressure chamber 210 which is located between a cover 212 of the outer housing 10 and the separator body 40 and is discharged therefrom by a pressure port 214.

The check valve 208 has a pre-chamber 216 arranged following the outlet 36, and following this a valve seat 218, on which a valve body 220 can be placed.

As can be seen in particular in FIG. 8, a central axis 222 of the outlet 36 is offset laterally relative to a central axis 224 of the prechamber 216, so that the outlet 36 as a whole opens asymmetrically into the prechamber 216. For this purpose, the pre-chamber 216 is provided with a cross-sectional area which is a multiple of the cross-sectional area of the outlet 36, so that the outlet 36 opens with the full cross-sectional area in a bottom 226 of the prechamber 216.

The pre-chamber 216 then extends below with its relative to the outlet 36 enlarged cross-sectional area to the valve seat 218 in the direction of the central axis 224, so that when lifted valve body 220 in the region of the valve seat 218, a passage opening 228 with a cross-sectional area of the antechamber 216 corresponding cross-sectional area for Flow through the valve seat 218 is available.

The valve body 220 is formed as a plate-shaped closed, that is formed without openings to an outer contour 238 extending body, wherein the outer contour 238 has a geometrically simple shape, such as a circle, but the shape can also be elliptical, rectangular, possibly formed with rounded corners his.

On a side opposite the antechamber 216, a movement space 230 for the valve body 220 rises above the valve seat 218 and has a central axis 232 which coincides with the central axis 224. The movement space 230 extends along the central axis 232 above the valve seat 218 up to a hub catcher designated as a whole by 240 which delimits the movement space 230 on a side opposite the valve seat 218. The cross-sectional area of the movement space 230 corresponds approximately to the cross-sectional area in the area of the valve seat 218, so that the valve body 220 moves freely in the movement space 230 between a closed position (FIG. 7), in which the valve body 220 rests on the valve seat 218, into an open position (FIG. 10) in which the valve body 220 rests against the lift catcher 240.

In order to guide the valve body 220 movable in the movement space 230, the movement space 230 follows the valve seat 218 parallel to the central axis 232 extending guide surfaces 242 which are formed in the simplest case by the movement space 230 bounding wall surfaces and are arranged for example at equal angular intervals from each other, to guide the valve body 220 in the direction of the central axis 232 of the movement space 230 on its peripheral side 238, so that in particular it is ensured that the valve body 220 comes to rest with the necessary precision in the transition from the open position to the closed position on the valve seat 218.

In order to allow outflow of gas refrigerant which has entered the movement space 230 through the prechamber 216 and the valve seat 218 from the movement space 230 when the valve body 220 is in the open position, as shown in FIG. 10, discharge spaces 244 are at the side of the movement space 230 provided, which open laterally via mouth openings 246 in the movement space 230, wherein the mouth openings 246 preferably extend from the Hubfänger 240 to the valve seat 218 in the direction of the central axis 232 and circumferentially around the central axis 232 each extend to the guide surfaces 242. Further, the outlet spaces 244 lead to the Hubfänger 240 facing outlet openings 248, which in turn pass into provided in the Hubfänger 240 passage openings 250, wherein the passage openings 250 in the Hubfänger 240 have a cross-sectional area which is greater than the cross-sectional area of the outlet openings 248 of the outlet spaces 244th has in the open position of the valve body 220 by the valve seat 218 in the moving space 230 entering gaseous refrigerant the opportunity to leave the movement space 230 through the orifices 246, to flow through the outlet 244 and from the Auslaßräumen 244 via the outlet openings 248 and the passage opening 250 in Hub catcher 240 enter the high pressure chamber 210.

The flow cross sections of the outlet chambers 244 and the outlet openings 248 and the passage openings 250 in Hubfänger are chosen so that the movement space 230 and the outlet chambers 244 flowing through gaseous refrigerant can flow around the valve body 220 standing in the open position and thereby contributes to the valve body 220 to move when opening the check valve 208 in the direction of the open position in which the valve body 220, for example, the Hubfänger 240 rests.

The valve body 220 in turn has an upper end face 252 facing the lift catcher 240, which extends preferably over the entire extent of the valve body 220 transversely to the central axis 232 to the outer contour 238 and in the case of the open position of the valve body 220 - as shown in FIG. abuts against a contact surface 254 of the Hubfängers 240, wherein the contact surface 254 has a surface area which is substantially the surface extent of the end face 252 corresponds, so that the end face 252 over the entire surface of the contact surface 254 of the Hubfängers 244 can be applied, in particular to avoid damage to the valve body 220 at a rapid transition from the closed position to the open position.

In order to move the valve body 220 rapidly from the open position to the closed position and in particular to be able to quickly lift any type of adhesion of the valve body 220 to the Hubfänger 240 by applying the end face 252 on the contact surface 254, the Hubfänger 240 is provided with an opening 260 which extends from a mouth opening 262 located in the abutment surface 254 of the lift catcher 240 to an upper side 264 of the lift catcher 240 facing the high pressure chamber 210 for applying a force present in the high pressure chamber 210 to a pressure drop in the movement space 230 the partial area of the end face 252 facing the break-through 260 and, when the valve body 220 is detached from the contact surface 254 with the end face 252, finally acting on the entire end face 252 by the pressure in the high-pressure chamber 210 Valve body 220 far from move the open position in the direction of the closed position in the movement space 230 in that a flowing back over the outlet 244 in the direction of the outlet 36 gaseous refrigerant flow 262 the valve body 220 additionally entrains and accelerates in the direction of the closed position, shown in Fig. 6 and 7 moves to to achieve a rapid closing of the check valve 208.

Preferably, the opening 260 is not arranged symmetrically to the central axis 232, but laterally offset with respect to this and that on a the central axis 222 of the outlet 36 opposite side of the central axis 232 and also within an angular range W about the central axis 232, which extends symmetrically to a plane E passing through the central axis 232 of the Bewegungsraurns 230 and the central axis 222 of the outlet 36 therethrough ,

As a result of this arrangement of the opening 260, when the end face 252 is detached from the abutment surface 254, the valve body 220 receives an asymmetrical application of force to the center axis 232, which results in the valve body 220 moving faster with the partial region of the end face 252 lying near the opening 260 the contact surface 254 lifts off than with the partial regions lying above the outlet 36, and thus the valve body 220 performs a slight tilting movement, which altogether promotes detachment of the end face 252 from the abutment surface 254 and, moreover, moves the valve body 220 more quickly into the coolant stream 262, which passes through the outlet spaces 244 and the movement space 230 in the direction of the prechamber 216, so that this refrigerant flow 262 accelerates the valve body 220 in the direction of the valve seat 218 and thus moves into the closed position.

In addition, the movement of the valve body 220 from the open position to the closed position can also be accelerated by the fact that the outlet 36 opens asymmetrically into the bottom 226 of the pre-chamber 216 and thus a total of both in the antechamber 216 and in the movement space 230 a to the central axis 232 asymmetric refrigerant flow 266 from the high-pressure chamber 210 in the direction of the outlet 36 forms, which additionally contributes to the valve body 220 after leaving the open position accelerated to move to the closed position. According to the invention, the check valve 208 is realized in that the outlet 36 and essentially the antechamber 216 are still seated within the bottom 20 of the compressor body 16, while in the integrally formed on the bottom 20 annular flange 42 of the valve seat 216, the movement space 230 and the outlet spaces 244th are incorporated, and finally the Hubfänger 240 is in the form of a lid on the annular flange 42.

The Hubfänger 240 has not only the described function in the inventive solution, but extends radially to the central axis 232 still so far in the direction of the annular flange 42 acting on the separating body 40, that the Hubfänger 240 effective between the annular flange 42 and the separating body 40 seal 270th engages, which lies in a ring flange 42 surrounding the groove 272 and a pressure-resistant connection between the annular flange 42 and the separator body 40 causes.

Claims

PATE NT CLAIM E

Compressor for refrigerants, comprising an outer casing (10), a in the outer casing (10) arranged scroll compressor (12) having a first fixed in the outer housing (10) compressor body (16) and a second, relative to the first compressor body (16) movable Compressor body (18), each having a bottom (20, 24) and above the respective bottom (20, 24) elevating first and second spiral ribs (22, 26) which engage in such that for compressing the refrigerant, the second compressor body (18) being movable relative to the first compressor body (16) to form chambers (28) on an orbital path about a central axis (46), an outlet (36) in the bottom (20) leading to a high pressure chamber (210) in the outer housing (10) ) of the stationary compressor body (16) and between the outlet (36) and the high pressure chamber (210) arranged check valve (208) having a valve body (220) which in a between ei a movement space (230) extending freely between a valve seat (218) closed position and an open position defined by the lift catcher (240), characterized in that the outlet (36) has a center axis (222) offset from a central axis (224) of the valve seat (218) for the valve body (220) in a transverse direction to the central axis (224).

2. A compressor according to claim 1, characterized in that a cross-sectional area of a passage opening (228) of the Ventilstitzes (218) is greater than a cross-sectional area of the outlet (36).

3. A compressor according to the preamble of claim 1 or claim 1 or 2, characterized in that between the valve seat (218) and the outlet (36) has a larger cross-sectional area than the outlet (36) having antechamber (216) is arranged.

4. A compressor according to claim 3, characterized in that the cross-sectional area of the pre-chamber (216) corresponds to at least one cross-sectional area of the passage opening (228).

5. A compressor according to claim 3 or 4, characterized in that a central axis (224) of the pre-chamber (216) is arranged offset transversely to the central axis (222) of the outlet (36).

6. A compressor according to claim 5, characterized in that the central axis (224) of the prechamber (216) substantially coincides with the central axis (224) of the valve seat (218).

7. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the movement space (230) with an approximately the valve seat (218) corresponding cross-sectional area in the direction of its central axis from the valve seat (218) to the Hubfänger (240) extends.

8. A compressor according to claim 7, characterized in that the central axis (232) of the movement space (230) substantially coincides with the central axis (224) of the valve seat (218).

9. A compressor according to any one of the preceding claims, characterized in that the valve body (220) is plate-shaped with an approximately the valve seat (218) corresponding outer contour (238) is formed.

10. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the side of the movement space (230) at least one outlet space (244) is arranged, which with an orifice (246) between the Hubfänger (240) and the Valve seat (218) opens laterally into the movement space (230) and leads to an outlet opening (248).

11. A compressor according to claim 10, characterized in that the mouth opening (246) of the outlet chamber (244) extends to the valve seat (218).

12. A compressor according to claim 10 or 11, characterized in that the outlet opening (248) in the region of the Hubfängers (240) is arranged.

13. A compressor according to claim 12, characterized in that the outlet opening (248) merges into a passage opening (250) in the Hubfänger (240).

14. A compressor according to any one of claims 10 to 13, characterized in that a plurality of outlet spaces (244) are arranged around the movement space (230) around.

15. A compressor according to any one of claims 10 to 14, characterized in that the movement space (230) by at least one next to the at least one mouth opening (246) lying wall surface (242) is limited.

16. A compressor according to claim 15, characterized in that the at least one wall surface forms a guide surface (242) for the valve body (220).

17. A compressor according to claim 16, characterized in that the valve body (220) through a plurality of the same angular distance about the central axis (232) of the movement space (230) arranged around guide surfaces (242) is guided.

18. A compressor according to any one of the preceding claims, characterized in that the Hubfänger (240) has a contact surface (254) for the valve body (220).

19. A compressor according to claim 18, characterized in that the valve body (220) has an end face (252), which is areally on the contact surface (254) of the valve body (220) can be applied.

20. A compressor according to claim 19, characterized in that the contact surface (254) has a surface area which is greater than half the surface area of the end face (252).

21. A compressor according to claim 20, characterized in that the contact surface (254) has a surface area which corresponds approximately to the surface area of the end face (252).

22. A compressor according to any one of claims 19 to 21, characterized in that the valve body (220) is plate-shaped and the end face (252) has a surface area which is more than half of an extension of the valve body (220) transversely to its central axis ( 232).

23. A compressor according to claim 22, characterized in that the surface extent of the end face (252) corresponds substantially to the cross-sectional area of the valve body (220).

24. A compressor according to the preamble of claim 1 or any one of the preceding claims, characterized in that the Hubfänger (240) with at least one opening (260) is provided, which from a in the contact surface (254) lying mouth opening (262) one of a high pressure side (264) of the Hubfängers (240) extends.

25. A compressor according to claim 24, characterized in that the at least one opening (260) laterally of the central axis (232) of the movement space (230).

26. A compressor according to claim 25, characterized in that the at least one aperture (260) in an angular segment (W) is arranged on one of the central axis (222) of the outlet (36) opposite side of the central axis (232) of the movement space ( 230) is located.

27. A compressor according to claim 26, characterized in that the angle segment (W) symmetrically to a through the central axis (222) of the outlet (36) and the central axis (232) of the movement space (230) passing through plane (E).

28. A compressor according to claim 27, characterized in that the angular segment (W) is approximately 150 °.

29. A compressor according to any one of the preceding claims, characterized in that the passage openings (250) in the Hubfänger (240) are outside of a movement space (230) final part of the same.