DE102012011278A1 - Ejector for refrigerant circuit of heat pump, has drive flow nozzle, which has opening in wall, where hole closer is arranged on wall, and opening is opened in position of hole closer - Google Patents

Abstract

The ejector (200) has a drive flow inlet (250), a drive flow nozzle (251), a mixing chamber (270), a suction flow inlet (240) and an ejector outlet (260). The drive flow nozzle has an opening in a wall, where a hole closer is arranged on the wall. The opening is opened in a position of the hole closer. The rotation range of the hole closer has another position, in which the hole closer partially covers the opening. The hole closer and the wall are connected with an axis, where the axis is arranged centrically to the drive flow nozzle. An independent claim is included for a method for operating a refrigerant circuit.

Description

The invention relates to an ejector for a refrigerant circuit with a Treibstromeintritt, a Treibstromdüse, a mixing chamber, a Saugstromeintritt and Ejektoraustritt. It furthermore relates to a refrigerant circuit in which at least one compressor, a gas cooler, an evaporator and an ejector arranged in the coolant circuit are provided, and a heat pump with an ejector contained in a refrigerant circuit.

Out US 2003/0145613 A1 an ejector for decompressing a refrigerant is known, which circulates in a refrigerant circuit. In the ejector, a needle valve is arranged, with which the decompression is controlled. A needle is inserted into a conical opening, depending on how much refrigerant should flow through the nozzle.

Out US 2005/0178150 A1 For example, an ejector cycle is known which includes an ejector. The ejector serves as a pressure reducing means for depressurizing a fluid, and also as a pulse feed pump for conveying the fluid by a entrainment action of an output high-speed working fluid. Such Ejektorpumpenkreis is effective z. B. Applicable to a refrigeration cycle of a vehicle air conditioning and cooling system, which performs a passenger compartment cooling climate operation and a refrigerator cooling operation using a plurality of evaporators.

US 2006/0266072 shows an ejector cycle device having a compressor that sucks and compresses a refrigerant, and a radiator that radiates heat of the high-pressure refrigerant discharged from the compressor. An ejector pump having a nozzle portion that converts a pressure energy of the high-pressure refrigerant on a downstream side of the radiator into a velocity energy to decompress and expand the refrigerant is provided. A suction port is included for sucking the refrigerant by a jet stream from the nozzle portion. A branch passage branches from a refrigerant passage between the radiator and the nozzle portion of the ejector, and is connected to the suction port of the ejector. A throttle unit is disposed in the branch passage, and the refrigerant is decompressed. An evaporator is disposed downstream of the throttling unit in the branch passage where the refrigerant evaporates. Accordingly, even if the ejector suction power is reduced at a low outside air temperature, it is possible to introduce refrigerant into the evaporator and maintain a cooling performance of the evaporator.

This ejector cycle device includes an ejector for a refrigeration cycle. There is provided a nozzle portion that reduces the pressure of a refrigerant to thereby expand the refrigerant. In a suction section, the refrigerant is sucked by the high-speed refrigerant discharged from the nozzle section and mixed in a diffuser section with the refrigerant sucked from the suction section. A first connection portion communicates with an upstream side of the nozzle portion, a second connection portion communicates with a downstream side of the diffuser portion, a third connection portion communicates with the suction portion, and a fourth connection portion communicates with an upstream side of the nozzle portion.

A control mechanism may control an opening of the nozzle portion. Alternatively, the control mechanism may be arranged to control an opening of a refrigerant passage passing through the fourth connection portion. Further, the known control mechanism may be provided with a needle disposed in a refrigerant passage of the nozzle portion, and an end of the refrigerant passage extending through the fourth connecting portion may be open on a side surface of the needle in the side facing away from the refrigerant passage of the nozzle portion. Alternatively, a throttle device may be provided to throttle a refrigerant flow passing through the fourth connection portion, e.g. For example, the throttle device may be disposed between the fourth connection portion and the first connection portion, or may be disposed in a refrigerant passage connected to the fourth connection portion.

The object of the invention is to improve an ejector so that a simple, safe and cost-effective control of the ejector is achieved. It is another object of the invention to provide a refrigerant circuit in which the ejector is integrated and in which an efficient operation of the refrigerant circuit is made possible.

The problem is solved by the features of claim 1.

In an ejector for a refrigerant cycle having a motive flow inlet, a motive flow nozzle, a mixing chamber, a suction flow inlet and an ejector outlet, the motive flow nozzle has at least a first opening in a wall. On the wall a hole sealer is arranged, which has a rotation area to the wall. The first opening is open in a first position of the hole sealer. The rotation area has a second one Position on, in which the hole closer at least partially covers the first opening. Advantageously, the hole sealer closes the first opening in the second position.

With this device, in particular the flow through the Treibstromdüse with refrigerant in the operation of a refrigerant circuit, in particular a heat pump is set. For this purpose, various positions are provided, in which the Lochverschließer can be brought. As far as all openings are open, the largest mass flow can flow through the Treibstromdüse. If the mass flow of refrigerant is to be reduced, then the openings are advantageously closed, depending on the predetermined mass flow one, advantageously two or more openings. However, it is also advantageous to keep at least one opening open in order to maintain a minimum mass flow at least during operation of the refrigerant circuit.

With an advantageous number of 1 + n openings in the wall, a number × openings are closed depending on a desired reduced mass flow. In case the maximum mass flow is desired, all 1 + n openings are open. In particular, two or more openings are closed in a more reduced desired mass flow.

Advantageously, the wall has a number of 1 + n openings, in particular at least one further fourth opening. The first opening is closed in the second position of the hole sealer, and the fourth opening is preferably open in the second position of the hole sealer.

According to one aspect of the invention, the wall has at least three openings, in particular a further second opening. In the rotation range is a third position. The hole sealer closes the first and fourth openings in the third position, and the second opening preferably remains open, whereby in the third position preferably two of at least three openings are closed. Other openings may be advantageously provided in the wall.

In an advantageous ejector for a refrigerant circuit having a driving flow inlet, a Treibstromdüse, a mixing chamber, a Saugstromeintritt and an ejector outlet, the Treibstromdüse at least a number of 1 + n openings in a wall. On the wall a hole sealer is arranged, which has a rotation area to the wall. A first opening is open in a first position of the hole sealer. The turning portion has a second position, and the hole sealer closes at least the first opening when in the second position.

According to a preferred concept of the invention, the turning region has at least one further third position or several additional positions, in which advantageously two or more of the 1 + n openings are closed and in particular at least one or more openings are open. In a second position, advantageously, groups of openings can be closed and at least one group of holes can be open.

The hole sealer and the wall are advantageously connected to an axle, so that the hole sealer or the wall is preferably rotatably mounted in a radial bearing at least in the rotation range.

The geometric axis of the ejector or the axis of the hole shooter is preferably located centrally with respect to the drive flow nozzle, and the hole sealer preferably has an asymmetrical wall with respect to the axis for closing the openings.

Advantageously, the at least first and second opening bores, which lie in particular symmetrically in the wall.

The inventive design of the Treibstromdüse a blocked flow is advantageously achieved in the motive nozzle, and the mach number of the flowing refrigerant is advantageously at 1. This has the advantage that the parameter mach number in the ejector is largely constant, in particular is 1, whereby in particular the mass flow over a wide range is known or can be determined and is processed in the control.

In an advantageous refrigerant circuit with at least one compressor, a heat exchanger, in particular a gas cooler or condenser, an evaporator and arranged in the Kältemittekreislauf ejector with a Treibstromeintritt, an ejector and a Saugstromeintritt, the Saugstromeintritt the ejector is connected to an evaporator outlet of the evaporator in connection so that during operation of the refrigerant circuit, a first refrigerant flow at a low pressure from the evaporator flows into the suction flow inlet of the ejector. The driving flow inlet communicates with the gas cooler outlet, so that a second refrigerant flow flows through the drive flow inlet into the ejector at a high pressure during operation of the refrigerant circuit. In the flow direction of the second refrigerant flow, a Treibstromdüse is arranged, which converts the pressure energy into a velocity energy, and thus the pressure of the second refrigerant flow is reduced. The ejector has a mixing chamber in which the second reduced in pressure during operation of the refrigerant circuit Refrigerant flow at least partially entrains the first refrigerant flow, wherein the first refrigerant flow is mixed with the second refrigerant flow to a mixed refrigerant flow, which is under a medium pressure.

The ejector outlet communicates with a separator inlet of a separator, whereby the refrigerant mixing stream flows during operation of the refrigerant circuit from the ejector to the separator.

In an advantageous method for operating a refrigerant circuit with a refrigerant, which is compressed in the operation of a compressor, is circulated in the refrigerant circuit and is at least partially expanded in an ejector, a first refrigerant flow flows from an expansion valve in which it is reduced to a low pressure, through an evaporator to a suction flow inlet of the ejector.

A second refrigerant stream flows at high pressure through a drive stream entry into the ejector. The second refrigerant flow is advantageously at least temporarily divided into a plurality of partial refrigerant jets in a drive flow nozzle and reduced and accelerated from high pressure to low pressure as it flows through the drive flow nozzle.

A division of the refrigerant jet is made by at least two or more holes in a wall of the Treibstromdüse.

The low pressure first refrigerant flow is entrained by the low pressure reduced and accelerated second refrigerant flow, and the first refrigerant flow is mixed with the second refrigerant flow to a mixed refrigerant flow which is under a medium pressure.

In an advantageous method, the refrigerant mixed stream flows during operation of the refrigerant circuit from the ejector to the separator and in particular has gaseous and liquid components.

The second refrigerant flow is advantageously reduced in the drive flow nozzle from a state (K3) with a high pressure to a state (K4) with the low pressure. From state (K4), there is an increase in enthalpy to a state (K5) where the second refrigerant stream is mixed with the first refrigerant stream at a low pressure to the refrigerant mixing stream, the refrigerant mixing stream at a diffuser loses velocity, and is raised from the gravure to a higher pressure than the gravure , wherein the refrigerant flow in the enthalpy advantageously further increases slightly.

If CO _{2 is used} as the refrigerant, the second refrigerant flow in the drive flow nozzle is advantageously reduced from the state (K3) with a high pressure of over 72 bar to the state (K4) with the low pressure. From the state (K4) with an enthalpy of about 200 to 260 kJ / kg enthalpy increase in the state (K5) with an enthalpy of about 300 to 380 kJ / kg, the second refrigerant flow with the first refrigerant flow at low pressure and at a Enthalpy between 260 and 380 kJ / kg is mixed to the mixed refrigerant flow, the refrigerant mixing flow in a diffuser loses speed and is raised by the gravure at about 30 to 40 bar to about 5-20% higher pressure than the gravure, wherein the refrigerant flow in the enthalpy advantageously further easily by up to 10 kJ / kg increases.

A heat pump has a refrigerant circuit according to one of the preceding claims 1 to 6, in particular operated according to one of the methods described above.

The concept of the invention will be explained with reference to the drawing. The figures show:

1 State diagram CO ₂

2 Refrigerant circulation

3 Schematic representation of an ejector

4 ejector

5 Sectional view ejector

6 Ejektorkopf

7 . 8th and 9 jet

10 Nozzle with hole sealer in position P1

11 Nozzle with hole sealer in position P2

12 Nozzle with hole sealer in position P3

13 Nozzle with hole sealer in position P4

14 Nozzle with hole sealer

15 Nozzle with hole sealer

16 Nozzle with hole sealer

17 Hole embodiments and number in the nozzle

18 nozzle shapes

19 Nozzle casing forms

20 control drives

1 shows a state diagram of a refrigerant R744 (CO ₂ ) with a critical point Kp. Starting from a state K1 with an enthalpy of about 410 kJ / kg and a pressure of about 40 bar, the refrigerant with a compressor 120 compressed to the state K2, wherein it has an enthalpy of about 480 kJ / kg and a pressure of about 130 bar in the state K2, but at least a pressure above 73 bar with at least one enthalpy, which is greater than in the state K1 , preferably at least 410 kJ / kg, in particular between 430 and 450 kJ / kg.

From state K2, the refrigerant passes through a gas cooler 130 cooled and loses enthalpy, in the embodiment of the state K2 with an enthalpy of about 480 kJ / kg to an enthalpy of about 250 kJ / kg; this is approximately isobaric. The gas cooler gives a heat quantity Q. _from ab.

Starting from the state K3, the refrigerant is brought into the state K4, wherein it further loses enthalpy of about 10 kJ / kg and in particular from a pressure of about 73 bar, in particular 130 bar, to less than 73 bar, in particular to about 35 bar is reduced. This pressure reduction takes place in a Treibstromdüse 251 an ejector 200 ,

Starting from the state K4, the refrigerant is then brought into the state K5. In doing so, it absorbs enthalpy from about 240 kJ / kg to about 335 kJ / kg. The enthalpy increase preferably takes place in a mixing chamber 270 of the ejector 200 ,

In the region of the state K5, a first refrigerant flow KS1 with a low pressure with a second refrigerant flow KS2, which was originally under high pressure, but now has gravure, mixed.

Starting from the state K5, a mixed refrigerant flow KM, which is formed from the first refrigerant flow KS1 and the second refrigerant flow KS2, in a diffuser 280 delayed. 10 kJ / kg, and the pressure increases in particular by about 5 bar, whereby in the state K10 in the refrigerant enthalpy of about 340 kJ / kg and a pressure of about 40 bar is included.

The present mixed refrigerant flow KM has gaseous and liquid refrigerant components. These are in a separator 160 separated, so that a gaseous refrigerant flow KMG is led to the state K1, from where again the compression takes place, and a liquid refrigerant flow KMF is led to Abscheideraustritt with the state K6, wherein the gaseous refrigerant in the separator 160 has an enthalpy of about 430 kJ / kg, and wherein the liquid refrigerant in the separator 160 has an enthalpy of about 210 kJ / kg.

In a throttle unit 150 the liquid refrigerant is reduced from the state K6 to the state K7, thereby reducing the pressure to about 37 bar. At these 37 bar, the refrigerant becomes an evaporator 140 supplied and gains in enthalpy, namely from about 210 kJ / kg to about 425 kJ / kg.

The first refrigerant flow KS1 now assumes the state K8 from the state K9 in that it is mitgesaugt with the second refrigerant flow KS2 and thereby there is a pressure drop and an enthalpy decrease of about 5 kJ / kg.

From state K9, the first refrigerant flow is transferred to state K5, in particular by mixing with the second refrigerant flow KS2.

In a refrigerant circuit 100 are different lines 110 . 111 . 112 . 113 and 114 intended. The refrigerant line 110 connects a compressor 120 with a gas cooler 130 , The refrigerant points in the refrigerant line 110 the state K2 and flows in the direction of ṁ _K in the gas cooler 130 the refrigerant is transferred from the state K2 in the state K3, where it - as described - heat Q. _from delivering. In the refrigerant line 111 the refrigerant has largely state K3.

In this state K3, it will enter the drive current 250 fed and then into the Treibstromdüse 251 , The Treibstromdüse 251 and the drive current entry 250 are in an ejector 200 arranged. Behind the Treibstromdüse 251 is a mixing chamber 270 arranged. In the mixing chamber 270 the second refrigerant flow KS2 is mixed with the first refrigerant flow KS1.

The refrigerant flow KS2 is in the refrigerant line 111 and the refrigerant flow KS1 in the refrigerant line 112 , The refrigerant line 112 is at a Saugstromteintritt 240 connected where the first refrigerant flow KS1 in a Saugstromdüse 241 of the ejector 200 is initiated. The first refrigerant flow KS1 and the second refrigerant flow KS2 mix in the mixing chamber 270 and then pour into a diffuser 280 where a mixed refrigerant flow KM formed of the first refrigerant flow KS1 and the second refrigerant flow KS2 loses in velocity.

After the diffuser 280 comes an ejector outlet 260 , and the refrigerant flows as Refrigerant mixing flow KM in the direction ṁ _KM through the pipe 114 to a separator 160 ,

In the refrigerant line 114 the refrigerant mixing flow KM has the state K10. The refrigerant flow KM passes through the separator inlet 161 in the separator 160 one. In the separator 160 there is a separation of gaseous parts and liquid parts of the refrigerant mixing stream KM.

The liquid portion of the refrigerant mixing flow KM is a throttle body 150 supplied and thus transferred from the state K6 in the state K7, which makes it in the refrigerant line 113 to the evaporator 140 flows.

The refrigerant line 113 is to an evaporator 140 connected, in which the refrigerant flows in the state K7 and in the evaporator 140 from state K7 to state K8. The evaporator 140 is to the refrigerant line 112 connected. The evaporator 140 takes a heat quantity Q. _to , wherein the refrigerant flows in the direction ṁ _s .

In principle, the ejector 200 at least one drive current entry 250 and a Treibstromdüse 251 on, like in 3 shown. A suction flow inlet 240 is preferably arranged laterally, it is followed by a Saugstromdüse 241 and a mixing chamber 270 , Furthermore, after the mixing chamber 270 a diffuser 280 and an ejector outlet 260 intended.

4 shows the ejector 200 , From the outside, the ejector points 200 a drive current entry 250 , a Saugstromteintritt 240 as well as an ejector outlet 260 on. Before the ejector outlet 260 are a mixing chamber 270 and a diffuser 280 intended. Furthermore, a sleeve nut 204 , a sleeve holder 223 as well as a final mother 222 intended.

5 shows an advantageous embodiment of the ejector 200 , The ejector 200 has an adjuster attachment 209 as well as an adjuster 208 on. A clasp 203 comes with seven Allen screws 225 held. An Einschrauber 227 provides a drive current entry 250 which is covered with copper gaskets 228 is sealed. A nozzle holder 201 is intended for mounting. With a locknut 205 becomes the at the nozzle holder 201 located sleeve nut 204 countered and fixed as needed.

To absorb the forces, in particular axially by screwing with hexagon socket screws 225 arise is in the ejector 200 a counterpart 202 intended. Another screwdriver 226 is as Saugstromteintritt 240 provided, which also with copper seals 228 is sealed.

The hole sealer 253 is with an axis 254 connected. With a sleeve holder 223 is a sleeve 211 fixed. Inside the ejector 200 is a grooved ring 230 provided, in particular in the area of the adjuster attachment 209 is arranged.

Furthermore, for sealing and mounting of the adjuster 208 as well as the axis 254 an O-ring 232 and a spring 224 intended. For coupling the adjuster attachment 209 is a hexagon socket screw 229 appropriate. In the sleeve holder nut 204 is a U-ring counterholder 210 as well as a grooved ring 231 contain. In the U-ring counterpart 210 is next to the grooved ring 231 an inlet suction side 212 enclosed.

copper gaskets 228 seal the nozzle by means of the surface 234c from the nozzle holder off. Outward to the sleeve 211 and to the inlet suction side 212 are O-rings 232 and 233 provided, in particular for sealing an inlet section 215 , The mixing chamber 270 is to the diffuser 280 with O-rings 232 sealed. A feather key 220 is between the sleeve 211 and the mixing chamber 270 and the diffuser 280 arranged. The diffuser 280 is with an O-ring 232 to a spacer sleeve 218 sealed. The spacer sleeve 218 is about a graduating mother 222 with a sleeve termination 219 connected, here again O-rings 232 serve for sealing. To the outside is still a copper seal 228 to at least one screwdriver 227 intended.

The nozzle 251 can have different embodiments. The 7 - 9 show different versions of the nozzle 251 with different openings. The in the 7 - 9 illustrated nozzles 251 are designed for the same refrigerant flow rate, so the hole is 251a according to 9 provided with a larger diameter than in 7 , The total required flow cross section results from the sum of the flow cross sections of the individual holes 251a . 251b . 251c . 251d and 251e ,

According to 8th have the holes 251a . 251b and 251c a total of the same cross-section as the five holes according to 7 , It may also be advantageous openings of the nozzle 251 to provide with different sized flow cross sections. It may also be advantageous that the sum of the cross-sections in a nozzle with a high number of holes must be greater than in the case of a nozzle with a small number of holes. The openings 251a - 251e are placed in a wall, and the wall 252 is located at the end of a nozzle shell 251x , For mounting, the nozzle casing 251x a paragraph 251z on, advantageously with a chamfer 251y ,

An advantageous Lochverschließer is in the 10 - 13 shown. The hole sealer 253 has a first segment 253a on, which is on the axis 254 located and between two flanks 253c and 253b has an angle β. In the direction of rotation spaced from the first segment 253a is a second segment 253d provided with a third flank 253e and a fourth flank 253f , where the third flank 253e and the fourth flank 253f are spaced over an angle γ. In the clockwise direction is after the second segment 253d a third segment 253g on the axis 254 attached.

The hole sealer 253 is preferably on the wall 252 at. The hole sealer 253 is rotatable about the axis 254 stored and rotatable at least at an angle α of a first position P1 in at least one further position P4. In the exemplary embodiment, the rotational range α from the position P1 to the position P4 is in particular approximately 50 °. Is the hole sealer 253 in position P1, are all existing openings 251a - 251e open.

According to 11 is the hole sealer 253 rotated through a rotational angle α 'in a position P2, where the first opening 251a is closed, the other openings 251b - 251e but still fully open.

According to 12 is the hole sealer 253 rotated by a rotational angle α '' in the position P3, so that also another opening, in this case the opening 251d , is closed and only the openings 251b . 251c and 251e are open.

According to 13 is the hole sealer 253 still further rotated by the rotation angle α, and also the opening 251c is closed, so according to 13 only two openings left 251b and 251e are open. In the present example, at least two openings should always be open in order to ensure a minimum refrigerant volume flow or mass flow.

The hole sealer 253 and the arrangement of the openings may, however, also look different. According to 14 are five openings 251a - 251e preferably arranged in a row, and the Lochverschließer 253 has a steadily rounded edge 253k on. By turning counterclockwise the openings become 251a to 251e closed one after the other depending on the position.

The hole sealer is with its axis 254 centric in front of the wall 252 arranged. In another embodiment according to 15 is an edge 253k provided, which also successively the openings 251a to 251e closes as soon as the hole sealer 253 is turned.

According to 16 the hole sealer is advantageous with a serrated or stepped edge 253k fitted.

The openings may represent various nozzle hole configurations and nozzle hole shapes.

Also the nozzle hole cross sections 251a may have a straight cross section, a conical cross section, a conical cross section on both sides or a cross section with an evaporation chamber 251f exhibit.

Also different nozzle shell shapes are advantageous, for. B. cylindrical, conical, rectangular or spherical. Also a split nozzle according to 19 is advantageously provided.

As a control drive and control mechanism for the adjuster 208 with which the hole sealer 253 is moved, electric stepper motors, an electromagnet or a temperature-controlled device are provided. A pressure control can be done via a spring or in the simplest case via a thumbwheel. The openings may in particular be designed as bores.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• US 2003/0145613 A1 [0002]
• US 2005/0178150 A1 [0003]
• US 2006/0266072 [0004]

Claims (13)

Ejector ( 200 ) for a refrigerant circuit ( 100 ) with a drive current inlet ( 250 ), a Treibstromdüse ( 251 ), a mixing chamber ( 270 ), a Saugstromteintritt ( 240 ) and an ejector outlet ( 260 ), wherein the drive flow nozzle ( 251 ) at least one first opening ( 251a ) in a wall ( 252 ), on the wall ( 252 ) a hole sealer ( 253 ), the hole sealer ( 253 ) to the wall ( 252 ) has a rotation range (α), the first opening ( 251a ) in a first position (P1) of the hole sealer ( 253 ) is open and the rotational range (α) has a second position (P2) in which the hole sealer ( 253 ) the first opening ( 251a ) at least partially covers. Ejector according to claim 1, characterized in that the wall ( 252 ) a number of 1 + n openings, in particular at least one further fourth opening ( 251d ), thus having at least two openings in the wall 252 the first opening ( 251a ) in the second position (P2) of the hole sealer ( 253 ) is closed and the fourth opening ( 251d ) in the second position (P2) of the hole sealer ( 253 ) is open. Ejector according to claim 2, characterized in that the wall has at least three openings ( 251a . 251b . 251d ), in particular a further second opening ( 251b ), in the rotation range (α) is a position (P3), the hole sealer ( 253 ) in the position (P3) the first and the fourth opening ( 251a . 251d ) and the second opening ( 251b ) is open, whereby in the position (P3) two of at least three openings are closed. Ejector ( 200 ) for a refrigerant circuit ( 100 ) with a drive current inlet ( 250 ), a Treibstromdüse ( 251 ), a mixing chamber ( 270 ), a Saugstromteintritt ( 240 ) and an ejector outlet ( 260 ), wherein the drive flow nozzle ( 251 ) at least a number of 1 + n openings in a wall ( 252 ), on the wall ( 252 ) a hole sealer ( 253 ), the hole sealer ( 253 ) to the wall ( 252 ) has a rotation range (α), a first opening ( 251a ) in a first position (P1) of the hole sealer ( 253 ), the rotation region (α) has a second position (P2) and the hole sealer ( 253 ) the first opening ( 251a ) at least closes when it is in the second position (P2). Ejector according to claim 4 or one of the preceding claims, characterized in that the rotation region (α) has at least one further position (P3) or a plurality of additional positions (P3, P4) in which two or more of the 1 + n openings are closed, and in particular at least one or more openings are open. Ejector according to one of the preceding claims, characterized in that the hole sealer ( 253 ) and the wall ( 252 ) with an axis ( 254 ), so that the hole sealer ( 253 ) or the wall ( 252 ) is rotatably mounted, preferably at least in the rotational range (α) in a radial bearing. Ejector according to claim 3, characterized in that the axis ( 254 ) Centric to the Treibstromdüse ( 251 ) and the hole sealer ( 253 ) preferably an asymmetric wall ( 252 ) with respect to the axis ( 254 ) having. Ejector according to claim 3, characterized in that the at least first and second openings ( 251a . 251b ) Are bores that lie in particular symmetrically in the wall. Refrigerant circulation ( 100 ) with at least one compressor ( 120 ), a gas cooler ( 130 ), an evaporator ( 140 ) and with a in the refrigerant circuit ( 100 ) arranged ejector ( 200 ) according to any one of the preceding claims, with a drive current inlet ( 250 ), an ejector outlet ( 260 ) and a Saugstromteintritt ( 240 ), characterized in that the Saugstromeintritt ( 240 ) of the ejector ( 200 ) with an evaporator outlet ( 142 ) of the evaporator ( 140 ), so that during operation of the refrigerant circuit ( 100 ) a first refrigerant flow (KS1) at a low pressure from the evaporator ( 140 ) in the Saugstromeintritt ( 240 ) of the ejector flows, - the driving current inlet ( 250 ) with the gas cooler outlet ( 131 ), so that a second refrigerant flow (KS2) at a high pressure in the operation of the refrigerant circuit ( 100 ) by the driving current inlet ( 250 ) in the ejector ( 200 ) flows, - in the flow direction of the second refrigerant flow (KS2) a Treibstromdüse ( 251 ) is arranged, in which then the pressure of the second refrigerant flow (KS2) is reduced, - the ejector ( 200 ) a mixing chamber ( 270 ), in which during operation of the refrigerant circuit ( 100 ) the second refrigerant stream (KS2) reduced in pressure at least partially entrains the first refrigerant stream, the first refrigerant stream (KS1) being mixed with the second refrigerant stream (KS2) to form a mixed refrigerant stream (KM) which is under a medium pressure, and Ejector outlet ( 260 ) with a separator entry ( 161 ) of a separator ( 160 ), whereby the mixed refrigerant flow (KM) during operation of the refrigerant circuit ( 100 ) from the ejector ( 200 ) to the separator 160 flows. Method for operating a refrigerant circuit ( 100 ) with a refrigerant, which in the operation of a compressor ( 120 ) in the Refrigerant circulation ( 100 ) and at least partially in an ejector ( 200 ), comprising the method steps, - that a first refrigerant flow (KS1) from an expansion valve ( 150 ), in which it is reduced to a low pressure, by an evaporator ( 140 ) to a Saugstromteintritt ( 240 ) of the ejector flows, - a second refrigerant flow (KS2) at a high pressure by a Treibstromeintritt ( 250 ) in the ejector ( 200 ) flows, - the second refrigerant flow (KS2) in a Treibstromdüse ( 251 ) is at least temporarily divided into a first partial refrigerant jet and a second partial refrigerant jet and when flowing through the Treibstromdüse ( 251 ) is reduced and accelerated from the high pressure to a gravure pressure, and - the low-pressure first refrigerant flow (KS1) is taken from the reduced to low pressure and accelerated second refrigerant flow KS2), and the first refrigerant flow (KS1) with the second refrigerant flow (KS2) to a mixed refrigerant stream (KM), which is under a medium pressure mixed. Method according to claim 7, comprising the method step that the mixed refrigerant flow (KM) during operation of the refrigerant circuit ( 100 ) from the ejector ( 200 ) to the separator ( 160 ) flows and advantageously has gaseous and liquid fractions. Method according to claim 7 or 8, comprising the method steps that the second refrigerant flow (KS2) in the drive flow nozzle ( 251 ) is reduced from a state (K3) with a high pressure of over 72 bar to a state (K4) with the low pressure, from the state (K4) with an enthalpy of about 200 to 260 kJ / kg an enthalpy increase to a state (K5) with an enthalpy of about 300 to 380 kJ / kg, wherein the second refrigerant flow (KS2) is mixed with the first refrigerant flow (KS1) at low pressure and at an enthalpy between 260 and 380 kJ / kg to the mixed refrigerant stream (KM) and the mixed refrigerant stream (KM) in a diffuser ( 280 ) Loses speed and is raised by the gravure with about 30 to 40 bar to about 5-20% higher pressure than the gravure, the refrigerant flow advantageously further increases in the enthalpy slightly by up to 10 kJ / kg. Heat pump with a refrigerant circuit according to one of the preceding claims 1 to 6, in particular operated according to a method according to one of claims 7 or 8.

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