DE102019208680A1 - Displacement machine based on the spiral principle, especially scroll compressors for a vehicle air conditioning system - Google Patents

Abstract

The invention relates to a scroll compressor (3), in particular for refrigerants in a vehicle air conditioning system, with a high-pressure chamber (29) and with compression chambers (24) formed between the spiral walls (21a, 21b) of a stationary and a movable scroll (21, 23) as well as with a Counter-pressure chamber (25) which is delimited from a low-pressure or suction side (26), a fluid channel (35) connected to at least one of the compression chambers (24) being provided in a base plate (21b) of the movable scroll (21), and wherein the counter-pressure chamber (25) is connected to the low-pressure or suction side (26) via a connecting channel (36).

Description

The invention is in the field of positive displacement machines according to the spiral principle and relates to a scroll compressor, in particular an electric motor, as a refrigerant compressor for a vehicle air conditioning system, according to the preamble of claim 1. Such a positive displacement machine and in particular such a scroll compressor is from the DE 10 2016 217 358 A1 or from the DE 10 2017 110 913 B3 known.

In motor vehicles, air conditioning systems are regularly installed, which air-condition the vehicle interior with the aid of a system that forms a refrigerant circuit. Such systems basically have a circuit in which a refrigerant is guided. The refrigerant, for example carbon dioxide (CO ₂ ) or R-134a (1,1,1,2-tetrafluoroethane) or R-744 (carbon dioxide), is heated in an evaporator and compressed by means of a (refrigerant) compressor, whereby the refrigerant then releases the absorbed heat again via a heat exchanger before it is routed to the evaporator again via a throttle.

Scroll technology is often used as a refrigerant compressor to compress a refrigerant-oil mixture. The resulting gas-oil mixture is separated, the separated gas being introduced into the air-conditioning circuit, while the separated oil can optionally be fed to the scroll compressor as a refrigerant compressor driven by an electric motor to lubricate moving parts.

The structure and mode of operation of such a scroll compressor for the refrigerant or the refrigerant-oil mixture of a motor vehicle air conditioning system is shown, for example, in FIG DE 10 2012 104 045 A1 and in "A Scroll Compressor for Air Conditioners", Tojo et al., Purdue e-Pubs (Purdue University), International Compressor Engineering Conference, 1984 described. A model calculation of a self-adjusting back-pressure or counter-pressure mechanism in a scroll compressor (scroll compressor) is in "Computer Modeling of Scroll Compressor with Self Adjusting Back-Pressure Mechanism", Tojo et al., Purdue e-Pubs (Purdue University), International Compressor Engineering Conference, 1986.

Essential components of the scroll compressor are a fixed scroll and a movable, orbiting scroll. The two scrolls (scroll parts) are basically constructed in the same way and each have a base plate and a spiral-shaped wall (wrap) extending from the base plate in the axial direction. In the assembled state, the spiral walls of the two scrolls lie one inside the other and form several compression chambers between the scroll walls that touch each other in sections.

An orbiting movement is to be understood here and below in particular as an eccentric, circular movement path in which the movable scroll itself does not rotate around its own axis. Thus, the scrolls are always at a minimum distance from one another, with each orbiting movement between the spiral walls forming the essentially sickle-shaped compression chambers, the volume of which is increasingly reduced (compressed) in the course of the movement.

When the movable scroll orbits, the sucked in gas-oil mixture arrives via an inlet to a first, radially outer compression chamber and from there via further compression chambers to the radially innermost compression chamber and from there via a central outlet, for example in the form of a bore, and possibly two adjacent secondary valves in the form of bores in the base plate of the stationary scroll into an outlet or high pressure chamber. The chamber volume in the compression chambers decreases from the radial outside to the radial inside, and the pressure of the increasingly compressing medium increases. During operation of the scroll compressor, the pressure in the compressor chambers thus rises from radially outside to radially inside.

During operation of the scroll compressor, due to the pressure generated in the compression chambers and the resulting axial force, the two scrolls are pressed apart, so that a gap and thus leakages can arise between the compression chambers. To avoid this as much as possible, the orbiting scroll is pressed against the stationary scroll. The corresponding axial force (counterforce) is generated in that a pressure chamber (back pressure chamber) is provided on the back of the base plate of the orbiting scroll, in which a specific pressure is generated.

This can be done in that a medium pressure channel (passage, opening, back pressure port) is introduced at a certain position in the base plate of the orbiting scroll, which connects at least one of the compression chambers formed by the scrolls with the back pressure chamber (back pressure chamber) so that refrigerant gas from the compression process between the scroll spirals flows directly into the counter-pressure or medium-pressure chamber. Due to the medium pressure channel in the movable scroll in connection with the The back pressure chamber is thus pressed against the stationary scroll in a self-adjusting manner (automatically) so that there is sufficient tightness (axial tightness). Alternatively, the medium pressure channel can be arranged in the fixed scroll and guided around the movable scroll to the counter pressure or medium pressure chamber.

It is essential in such systems that the pressure in the back pressure chamber can adaptively adapt to the respective operating point of the scroll compressor. This means that a different pressure must prevail in the back pressure chamber at an operating point or pressure ratio of suction pressure (low pressure) with 3 bar to high pressure with 15 bar than at an operating point or pressure ratio of suction pressure (low pressure) with 3 bar to high pressure with 25 bar. This adaptive adjustment can be achieved by fluidic components in the form of ball check valves, orifices or nozzles.

From the EP 2 369 182 B1 a scroll compressor with a housing is known in which a stationary scroll with a base plate and a spiral formed thereon and a movable scroll rotating around an axis of rotation with a base plate and a spiral formed thereon are arranged. A dispensing chamber (high pressure chamber) is formed between the base plate of the stationary scroll and a housing section. An intermediate bearing wall with a shaft bearing arranged in the housing delimits a suction or inlet chamber (low pressure chamber) and forms a backpressure chamber with the base plate of the movable scroll, which communicates with the compression chamber between the scrolls via a delivery channel in the movable scroll. The dispensing chamber and the back pressure chamber are in communication via a secondary delivery channel which extends substantially axially through an outer wall of the stationary scroll. The secondary delivery channel supplies oil or coolant gas separated in the delivery chamber by means of an oil separator into the back pressure chamber in order to restore the pressure in the back pressure chamber in a short time after a pressure drop.

The invention is based on the object of specifying a particularly suitable scroll compressor, in particular driven or drivable by an electric motor, as a refrigerant compressor for a vehicle air conditioning system. In particular, a flexible and effective adjustment of the pressure in the backpressure chamber to operating points of the scroll compressor for a vehicle air conditioning system, preferably in cooling and heat pump mode, is to be achieved through a channel system (pressure channel system) that is as simple as possible, preferably small-scale or cost-saving.

This object is achieved according to the invention by the features of claim 1. Advantageous configurations and developments are the subject of the subclaims.

For this purpose, the scroll compressor, in particular for refrigerants of a vehicle air conditioning system, has a housing with a high pressure chamber and with compression chambers and with a counter pressure chamber which is separated from a low pressure or suction side by means of a partition (center plate). Furthermore, the scroll compressor has a stationary scroll and a movable (orbiting) scroll, each with a base plate and a spiral wall, the spiral walls interlocking, that is to say being nested, and thereby forming compression chambers. In the base plate of the movable scroll a fluid channel is provided which is in communication with at least one of the compression chambers. In addition, the counter-pressure chamber is connected to the low-pressure or suction side via a connection channel.

The connecting channel is preferably made in the partition. The connecting channel is expediently oriented radially (in the radial direction). The connecting channel is also advantageously designed as a bore in the partition. The connection channel from the counter-pressure chamber to the low-pressure or suction side is also advantageously effective as a flow-regulating nozzle.

In an advantageous embodiment, the fluid channel connected to the compression chamber, starting from the entry into the spiral wall (spiral start) of the movable scroll, is at a spiral angle ( φ ) from 360 ° to 390 °, preferably from 380 ° to 385 °. The fluid channel between the compression chamber and the counter-pressure chamber is also preferably designed as a bore. Similarly, the fluid channel between the compressor chamber and the back pressure chamber also acts as a flow-regulating nozzle.

The invention also relates to a refrigerant compressor which has an electromotive drive module with a drive housing and a compressor module in the form of the scroll compressor, with a low-pressure chamber being formed within the drive housing into which the connecting channel to the counter-pressure chamber opens. In this case, the high pressure chamber and the low pressure chamber are preferably connected via a fluid line, a fluid channel or a connecting channel. This fluid line is used for the return of in the high pressure chamber oil separated from the refrigerant-oil mixture into the low-pressure chamber.

The advantages achieved with the invention are in particular that with only two channels, which connect the backpressure chamber (counter pressure chamber) on the one hand with one of the compression chambers and on the other hand with the suction or low pressure chamber, a functional advantage over known systems in terms of efficiency and possible uses of the Scroll compressor at low cost. Since only two small bores are expediently to be drilled into the base plate of the movable scroll on the one hand and in the partition between the back pressure chamber (counter pressure chamber) and the suction or low pressure chamber, a considerable cost advantage is also achieved due to the simple and component-saving design.

These two channels create a certain static pressure in the connection (line) between the corresponding compression chamber and the backpressure chamber (counterpressure chamber), which then also acts in the backpressure chamber (counterpressure chamber). The design or effect of these channels as flow-regulating nozzles enables simple and effective adaptive control of the pressure in the back pressure chamber (counter pressure chamber).

This adaptive control behavior can be achieved through the targeted positioning of the channels (bores, nozzles) and the targeted combination of their channel or bore diameter, i.e. H. certain ratios of the channel or bore diameter can be set in order to ensure the reliable functioning of different variants and sizes of scroll compressors, depending on the stroke volume and, as a result, differently dimensioned scroll components.

Furthermore, due to the adaptive adjustment of the pressure in the backpressure chamber, the scroll compressor can be operated with high efficiency at operating points in cooling and heat pump mode, because in particular leaks are reduced and friction losses between the scroll parts are kept to a minimum. The axial force effective as a result of the self-adjusting pressure in the counterpressure chamber is always only a small amount greater than the sum of the axial forces in the compression chambers due to the adaptive adaptation. Furthermore, this self-adjusting system creates a variable pressure in the back pressure chamber, i. if necessary a higher or lower back pressure.

In contrast to a system in which a regulating fluid mass flow is taken from the high-pressure chamber, the present system offers an energetic advantage, since the regulating fluid mass flow taken from the corresponding compression chamber has not yet been fully compressed. In addition, due to the comparatively low pressure difference, no high manufacturing accuracy is required when producing the connecting channel between the back pressure chamber and the low pressure chamber (suction side).

• 1 in einer perspektivischen Seitenansicht einen Scrollverdichter mit einem elektromotorischen Antriebsmodul und mit einem Verdichtermodul,
• 2 in einer Schnittdarstellung schematisch vereinfacht den elektromotorisch angetrieben Scrollverdichter mit einer Hochdruckkammer und mit einer Gegendruckkammer (Back-Pressure-Kammer) sowie mit in diesen führenden Kanälen,
• 3 in einer Schnittdarstellung den Scrollverdichter mit in einem Verdichtergehäuse einem feststehenden und einem beweglichen Scroll sowie mit einem in die Gegendruckkammer führenden Fluidkanal aus einer Verdichterkammer und einem Verbindungskanal zu einer saugseitigen Niederdruckkammer,
• 4 in einem Blockschaltbild eine Ölrückführung aus der Hochdruckkammer in die Niederdruckkammer sowie die als Düsen wirksamen Kanäle von der Gegendruckkammer in die Verdichterkammer und in die Niederdruckkammer, und
• 5 in einer Draufsicht den beweglichen (orbitierenden) Scroll mit in einer eingezeichneten Winkelposition (Spiralwinkel) den zu der Verdichterkammer führenden Verbindungskanals in der Basisplatte des beweglichen Scrolls.

An exemplary embodiment of the invention is explained in more detail below with reference to a drawing. Show in it:

• 1 in a perspective side view a scroll compressor with an electromotive drive module and with a compressor module,
• 2 in a sectional view, schematically simplified, the scroll compressor driven by an electric motor with a high pressure chamber and with a back pressure chamber and with ducts leading into these,
• 3 in a sectional view of the scroll compressor with a stationary and a movable scroll in a compressor housing and with a fluid channel leading into the counter-pressure chamber, comprising a compression chamber and a connection channel to a suction-side low-pressure chamber,
• 4th in a block diagram an oil return from the high-pressure chamber into the low-pressure chamber and the channels from the counter-pressure chamber into the compression chamber and into the low-pressure chamber, which act as nozzles, and
• 5 in a top view the movable (orbiting) scroll with the connection channel leading to the compression chamber in a drawn angular position (spiral angle) in the base plate of the movable scroll.

Corresponding parts and sizes are always provided with the same reference symbols in all figures.

The in 1 refrigerant compressor shown 1 , which can be installed in a refrigerant circuit (not shown) of an air conditioning system of a motor vehicle, has an electric (electromotive) drive module 2 and a compressor module in the form of a scroll compressor coupled to it 3 on. Via a (mechanical) interface 4th between the drive module 2 and the scroll compressor 3 is this to the drive module 2 tied up. The mechanical interface 4th serves as the drive end shield and forms a partition 5 ( 2 and 3 ). The scroll compressor 3 is by means of circumferentially distributed, in the axial direction A. of the refrigerant compressor 1 extending flange connections 6th with the drive module 2 connected, in particular screwed.

A housing section of a drive housing 7th of the refrigerant compressor 1 is as a motor housing 7a to accommodate an electric motor 13th formed and on the one hand by an integrated housing partition 7b to one with a housing cover 7c provided electronics housing 7d with one the electric motor 13th controlling engine electronics (electronics) 8th and on the other hand through the mechanical interface 4th with the end shield and the partition 5 locked ( 2 ). The drive housing 7th points in the area of the electronics housing 7b a connection section 9 with to electronics 8th guided motor connections 9a and 9b for electrical contacting of the electronics 8th to an electrical system of the motor vehicle.

The drive housing 7th has a refrigerant inlet or refrigerant inlet 10 for connection to the refrigerant circuit and a refrigerant outlet 11 on. When connected, it forms the inlet 10 in the 2 with 26 designated low pressure or suction side and opens into an in 2 with 26 'designated low pressure chamber of the refrigerant compressor 1 a. The outlet 11 forms the high pressure or pump side (pump side) of the refrigerant compressor 1 .

2 shows schematically the electromotive refrigerant compressor 1 in a sectional view along an axis of rotation 14th the electric motor designed as a brushless direct current motor (BLDC) 13th with cylindrical rotor 15th . This is circumferentially by means of a hollow cylindrical stator 16 surround. The rotor 15th , which comprises a number of permanent magnets, is by means of a shaft 17th rotatable around the axis of rotation 14th stored. The stator 16 has a number of electrical coils, which by means of electronics 8th are energized, which is connected, for example, to a bus system and to the electrical system of the motor vehicle.

The Electronic 8th is in the electronics housing 7d of the drive housing 7th arranged. The engine electronics 8th has circuit boards 18th , 19th on that in the axial direction A. are arranged one above the other. A bridge circuit of the circuit board 18th which is the partition between the housing 7b closest is is over through the enclosure partition 7b guided power supply lines 20th with the electric coils of the stator 16 contacted. The bridge circuit is fed by means of the on-board network and by means of a control circuit on the other printed circuit board 19th which is connected to the bus system in terms of signaling.

How in connection with 3 can be seen, the scroll compressor 3 one in the compressor housing 12 arranged movable scroll (scroll part) 21st on. This is via an eccentric shaft journal 17a with, for example, two joining pins, only one of which is joining pins 17b is visible to the shaft 17th of the electric motor 13th coupled that into the mechanical interface 4th is guided with A-side end shield. The eccentric shaft journal 17a is in a moving scroll 21st held roller or ball bearings 22a stored. Another roller or ball bearing 22b for the shaft 17th is in the mechanical interface serving as the A-side end shield 4th and there in the partition 5 arranged. The moving scroll (scroll part) 21st is in operation of the scroll compressor 3 orbiting driven.

The scroll compressor 3 also has a rigid in the compressor housing 12 attached fixed scroll (scroll part) 23 on. The two scrolls (scroll parts) 21st , 23 grip with their helical or spiral scroll walls (scroll spirals) 21a , 23a into each other by a respective base plate 21b , 23b rise axially. Between the scrolls 21st , 23 , ie between their scroll walls or scroll spirals 21a , 23a and the base plates 21b , 23b are compression chambers 24 formed, their volume when the electric motor is in operation 13th is changed.

Between the A-side end shield and the movable scroll 21st is located in the partition 5 or limited by a counter-pressure chamber (back-pressure chamber) 25th . This is in the compressor housing referred to below simply as the housing 12 from the base plate 21b of the moving scroll 21st and / or from an intermediate plate (wear plate) 5a ( 3 ) in the form of a steel plate, which has good sliding properties for the orbiting scroll 21st having. The back pressure chamber 25th extends into the base plate in some areas 21b of the moving scroll 21st inside.

During operation, the refrigerant is drawn through the inlet 10 in the drive housing 7th and there in the motor housing 7a initiated. This area of the drive housing 7th with the lower chamber 26 ' forms the suction or low pressure side 26th of the scroll compressor 3 . Inside the drive housing 7th the refrigerant is mixed with oil present in the refrigerant circuit and along the rotor 15th and the stator 16 through one or more openings 27 ( 3 ) in the partition 5 to the scroll compressor 3 sucked. Using the scroll compressor 3 the mixture of refrigerant and oil is compressed. The oil is used to lubricate the two scrolls 21st , 23 so that friction is reduced and hence the efficiency is increased. The oil also serves as a seal to prevent uncontrolled escape of the between the two scrolls (scroll parts) 21st , 23 to avoid any refrigerant.

The compressed mixture of refrigerant and oil is released via a central outlet 28 in the base plate 23b of the fixed scroll 23 in a high pressure chamber 29 inside the compressor housing 12 directed. In the high pressure chamber 29 there is an oil separator (cyclone separator) 30th . The heavier oil of the mixture of refrigerant and oil is in a lower area of the oil separator 30th collected while the refrigerant is up or sideways through the outlet 11 is discharged. The separated oil is from the high pressure chamber 29 into the low pressure chamber 26th returned. The high pressure chamber is used for this 29 and the low pressure chamber 26 ' via a fluid line 31 connected to the oil return. In the fluid line 31 can be a throttle body 32 be provided.

As in 3 can be seen comparatively clearly, which is in the radially innermost chamber area 24 ' the compression chambers 24 located central outlet 28 going into the high pressure or discharge chamber 29 opens into the base plate 23b of the fixed scroll 23 introduced as a hole. Inside the high pressure chamber 29 is the central outlet 28 with a spring valve (finger spring valve) 33 closed as long as the pressure in the compression chambers 24 is less than the pressure in the high pressure chamber 29 . Is the pressure of the compressed refrigerant-oil mixture in the compression chambers 24 , 24 ' greater than the pressure in the high pressure chamber 29 , the spring valve opens 33 almost automatically.

A stop element 34 that is in the high pressure chamber 29 on the fixed scroll 23 , for example on its base plate 23b , is attached, limits the stroke of the spring valve 33 . When the pressure is below the pressure in the high pressure chamber 29 has sunk, the spring valve closes 33 the outlet 28 again automatically due to its spring preload. In this way, the compressed refrigerant-oil mixture arrives - depending on the speed of the shaft 17th or depending on the operating point of the scroll compressor 3 - continuously (continuously) or intermittently or pulsating via the central outlet 28 from the compression chambers 24 into the high pressure chamber 29 .

In the base plate 21b of the moving (orbiting) scroll 21st is a fluid channel 35 provided over which one of the compression chambers 24 fluidically with the back pressure chamber 25th communicates (is connected). The fluid line 35 is designed in a simple manner as a bore and effective as a flow-regulating nozzle.

Furthermore is in the partition wall 5 a connecting channel 36 provided over which the back pressure chamber 25th with the suction side 26th communicates and there with the low pressure chamber 26 ' is fluidically connected. Also the connection channel 36 is designed in a simple manner as a bore and effective as a flow-regulating nozzle. The connecting channel 36 is located in a cylindrical collar portion 5b of the partition 5 and is according to the embodiment according to 3 preferably in the radial direction R. oriented. The collar portion 5b, which extends in the axial direction A. extends, forms the bearing seat for the shaft bearing (roller or ball bearing) 22b .

4th shows schematically in a block diagram the fluidic (pressure-bearing) connection of the back pressure chamber 25th with one of the compression chambers 24 and with the suction side 26th via that from the fluid channel 35 and the connection channel 36 formed canal system. The position of the hole in the base plate 21b of the moving scroll 21st introduced fluid channel, its nozzle symbol also with the reference number 35 is provided with P ₃₅ designated. The angle between this position P ₃₅ and the entrance (spiral start) 21c into the spiral wall 21a of the moving scroll 21st is with α designated.

Also in 4th the connection channel is illustrated 36 between the back pressure chamber 25th and the suction-side low-pressure chamber 26 ' , again its nozzle symbol with the reference number 36 is provided. Furthermore, the oil return shown as a broken (dashed) line is shown 31 from the high pressure chamber 29 in the area of the oil separator 30th into the low pressure chamber (suction chamber) 26 ' illustrated.

The cross-sectional area of the connecting channel 36 and the fluid channel 35 is many times, for example ten times, smaller than the cross-sectional area of the central outlet 28 . The diameter of the central outlet 28 is for example between 5 mm and 10 mm. The preferably circular cross-sectional areas of the connecting channel 36 and the fluid channel 35 can be the same or different.

With the one from the connecting channel 36 and the fluid channel 35 The channel system formed is a particularly effective (adaptive) flow control of the (static) pressure in the back pressure chamber 25th reached. Due to the static pressure prevailing within the counter-pressure chamber during operation 25th is the moving scroll 21st pressurized and is, as by the with F _G indicated force arrows illustrated along the axis of rotation 14th against the stationary scroll 23 pressed. This force (counterforce) F _G acts the axial force illustrated by the force arrows F _V contrary to the result of the in the compression chambers 24 prevailing pressure in turn on the movable scroll 21st works. Together with that from the corresponding compression chamber 24 via the fluid channel 35 to the back pressure chamber 25th transmitted (transmitted) pressure is approximately an equilibrium of forces (F _G ≥ F _V ) and thus the desired sealing effect between the two scrolls 21st , 23 one, being the opposing force F _G is or should be only slightly greater than the axial force F _V .

5 shows the movable scroll in a plan view 21st with the channel 35 that is in the base plate 21b on the inside of the scroll wall (scroll spiral) 21a predetermined angular position P ₃₅ is arranged. The position P ₃₅ this channel 35 is located starting from the beginning of the spiral 21c the spiral wall 21a of the moving scroll 21st preferably with the spiral angle drawn in as an angle line φ , with φ = (380 ± 10) °, preferably φ = (383 ± 2) °. The beginning of the spiral 21c is about 5 ° to 10 ° clockwise behind (after) the dash-dotted vertical line A _V . The also in 4th drawn angle α is between 15 ° and 20 °.

In summary, the scroll compressor, which is provided and set up in particular for refrigerants in a vehicle air conditioning system 3 in a compressor housing 12 with a high pressure chamber 29 and with compression chambers 24 as well as with a counter pressure chamber (back pressure chamber) 25th a fixed scroll 23 and a movable scroll that orbits during compressor operation (oscillating, rolling movement) 21st on. The scrolls form 21st , 23 each having a base plate 21b , 23b and a scroll or spiral wall integral therewith (molded onto it) 21a , 23a have, between their interlocking scroll or spiral walls 21a or. 23a the compression chamber (s) 24 . The base plate 23b of the fixed scroll 23 limits the high pressure chamber 27 , and the base plate 21b of the moving scroll 21st limits the back pressure chamber 25th . The back pressure chamber 25th stands over one in the base plate 21b of the orbiting scroll 21st introduced first channel 35 with at least one of the compression chambers 24 and a second channel 36 with the suction side 26th or with the low pressure chamber 26 ' (fluidic) in connection.

This arises or prevails in the first channel for operational reasons 35 , over which the back pressure chamber 25th fluidically with one of the compression chambers 24 communicates, one also in the back pressure chamber 25th acting static pressure. The execution of the two channels 35 and 36 as simple bores and their effect as flow-regulating nozzles enables simple and effective (adaptive) control of the pressure in the backpressure chamber 25th . This adaptive control behavior is achieved through the targeted positioning of the channels (bores, nozzles) 35 and 36 and their specifically selected channel or bore diameter (cross-sectional areas). As a result, a reliable function of different variants and sizes of scroll compressors can be ensured. In addition, the scroll compressor 1 due to the adaptive adjustment of the pressure in the back pressure chamber 25th can be operated with high efficiency at operating points in cooling and heat pump mode.

The invention thus relates to a scroll compressor 3 , in particular for refrigerants in a vehicle air conditioning system, with a high-pressure chamber 29 and with between the spiral walls 21a , 21b a fixed and a moving scroll 21st , 23 formed compression chambers 24 as well as with a counter pressure chamber 25th , being in a base plate 21b of the moving scroll 21st one with at least one of the compression chambers 24 connected fluid channel 35 is provided, and wherein the back pressure chamber 25th via a connection channel 36 with the suction side 26th and / or with the low pressure chamber 26 ' of the refrigerant compressor 1 connected is.

The invention also relates to a refrigerant compressor 1 , which is an electromotive drive module 2 with a drive housing 7th and a compressor module in the form of the scroll compressor 3 having, within the drive housing 7th a low pressure chamber 26 ' is formed into which the connecting channel 36 to the back pressure chamber 25th joins. The high pressure chambers are preferred 29 and the low pressure chamber 26 ' via a fluid line 31 connected to the oil return.

The claimed invention is not restricted to the exemplary embodiments described above. Rather, other variants of the invention can also be derived therefrom by the person skilled in the art within the scope of the disclosed claims without departing from the subject matter of the claimed invention. In particular, all the individual features described in connection with the various exemplary embodiments can also be combined in other ways within the scope of the disclosed claims without departing from the subject matter of the claimed invention.

List of reference symbols

1

Refrigerant compressor

2

Drive module

3

Scroll compressor / compressor module

4th

interface

5

Bearing shield / partition

5a

Intermediate plate / ware plate

6th

Flange connection

7th

Drive housing

7a

Motor housing

7b

Housing partition

7c

Housing cover

7d

Electronics housing

8th

Engine electronics

9

Connection section

9a, b

Motor connection

10

Inlet / inlet

11

Outlet

12

Compressor housing

13

Electric motor

14th

Rotor axis

15th

rotor

16

stator

17th

wave

17a

Shaft journal

17b

Joining pin

18.19

Circuit board

20th

Power supply line

21st

moving / orbiting scroll / part

21a

Scroll wall / spiral

21b

Base plate

21c

Entrance / beginning of spiral

22a, b

Roller / ball bearings

23

fixed scroll / part

23a

Scroll wall / spiral

23b

Base plate

24

Compression chamber

24 '

Chamber area

25th

Counter pressure / back pressure chamber

26th

Suction / low pressure side

26 '

Low pressure chamber

27

opening

28

central outlet

29

High pressure / discharge chamber

30th

Oil separator

31

Fluid line

32

Throttle body

33

Spring valve

34

Stop element

35

Fluid channel

36

Connection channel

α

angle

φ

Spiral angle

A.

Axial direction

A _V

Vertical line

F _G

Counterforce

F _V

Axial force

P ₃₅

Position of the fluid channel

R.

Radial direction

QUOTES INCLUDED IN THE DESCRIPTION

This list of the documents listed by the applicant was 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.

Patent literature cited

• DE 102016217358 A1 [0001]
• DE 102017110913 B3 [0001]
• DE 102012104045 A1 [0004]
• EP 2369182 B1 [0011]

Non-patent literature cited

• Tojo et al., Purdue e-Pubs (Purdue University), International Compressor Engineering Conference, 1984 [0004]

Claims (10)

Scroll compressor (3), in particular for refrigerants of a vehicle air conditioning system, comprising - a housing (12) with a high-pressure chamber (29) and with compression chambers (24) and with a counter-pressure chamber (25), which by means of a partition (5) of a low-pressure or Suction side (26), - a stationary scroll (23) with a base plate (23b) and with a spiral wall (23a), - a movable scroll (21) with a base plate (21b) and with a spiral wall (21a), which engages in the spiral wall (23b) of the stationary scroll (23) and forms the compression chambers (24) with it, a fluid channel (35) connected to at least one of the compression chambers (24) in the base plate (21b) of the movable scroll (21) is provided, characterized in that the counter-pressure chamber (25) is connected to the low-pressure or suction side (26) via a connecting channel (36). Scroll compressor (3) Claim 1 , characterized in that the counter-pressure chamber (25) is separated from the low-pressure or suction side (26) by means of a partition (5) and the connecting channel (36) is introduced into the partition (5). Scroll compressor (3) Claim 1 or 2 , characterized in that the connecting channel (36) is oriented in the radial direction (R). Scroll compressor (3) after one of the Claims 1 to 3 , characterized in that the connecting channel (36) from the counter-pressure chamber (25) to the low-pressure or suction side (26) is designed as a bore. Scroll compressor (3) after one of the Claims 1 to 4th , characterized in that the connecting channel (36) from the counter-pressure chamber (25) to the low-pressure or suction side (26) acts as a flow-regulating nozzle. Scroll compressor (3) after one of the Claims 1 to 5 , characterized in that the fluid channel (35) connected to the compression chamber (24) starting from the inlet (21c) in the spiral wall (21a) of the movable scroll (21) at a spiral angle (φ) of 360 ° to 390 °, preferably of 380 ° to 385 °, is arranged. Scroll compressor (3) after one of the Claims 1 to 6th , characterized in that the fluid channel (35) between the compression chamber (24) and the back pressure chamber (25) is designed as a bore. Scroll compressor (3) after one of the Claims 1 to 7th , characterized in that the fluid channel (35) between the compression chamber (24) and the counter-pressure chamber (25) acts as a flow-regulating nozzle. A refrigerant compressor (1), comprising an electromotive drive module (2) with a drive housing (7) and a compressor module in the form of a scroll compressor (3) according to one of the Claims 1 to 8th wherein a low-pressure chamber (26 ') is formed within the drive housing (7), into which the connecting channel (36) to the counter-pressure chamber (25) opens. Refrigerant compressor (1) after it Claim 9 , characterized in that the high pressure chamber (29) and the low pressure chamber (26 ') are connected via a fluid line (31) for oil return.

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