WO2022058304A1

WO2022058304A1 - Scroll compressor for coolant for a vehicle air conditioning system

Info

Publication number: WO2022058304A1
Application number: PCT/EP2021/075223
Authority: WO
Inventors: Björn FAGERLI; Budi Rinaldi; Dennis RYMA; Maximilian Fingas
Original assignee: Brose Fahrzeugteile SE & Co. Kommanditgesellschaft, Würzburg
Priority date: 2020-09-18
Filing date: 2021-09-14
Publication date: 2022-03-24
Also published as: DE102020211707A1; CN115989365A

Abstract

The invention relates to a scroll compressor (6) for coolant for a vehicle air conditioning system, having two scrolls (24, 26) which are movable in opposition to one another, each have a base plate (24b, 26b), and each have a spiral wall (24a, 26a), the spiral walls (24a, 26a) engaging in one another and forming compressor chambers (28), the spiral walls (24a) having a spiral tip (24c) as axial contact face against the other base plate (26b), one of the spiral walls (24a) having a spiral end region (32) which is drawn in axially with respect to the corresponding spiral tip (24a).

Description

description

Scroll compressor for refrigerant of a vehicle air conditioning system

The invention is in the field of displacement machines based on the spiral principle and relates to a scroll compressor for an electrical cold medium drive, in particular as a refrigerant compressor for refrigerants in a vehicle air conditioning system.

Air conditioning systems are regularly installed in motor vehicles, which air-condition the vehicle interior with the aid of a system forming a refrigerant circuit. Such systems basically have a circuit in which a refrigerant is guided. The refrigerant, for example R-744 (carbon dioxide, CO2) or R-134a (1,1,1,2-tetrafluoroethane), is heated in an evaporator and compressed by means of a (refrigerant) compressor or compressor, with the refrigerant then being a heat exchanger gives off the absorbed heat again before it is fed back to the evaporator via a throttle.

Scroll technology is often used as a refrigerant compressor to compress a refrigerant-oil mixture. Most of the resulting gas-oil mixture is separated, and the separated gas is fed into the air-conditioning circuit. If necessary, the separated oil can be fed to the moving parts within the scroll compressor as a refrigerant compressor, suitably driven by an electric motor, for lubricating them.

The construction and functioning of such a scroll compressor for the refrigerant or the refrigerant-oil mixture of a motor vehicle air-conditioning system is described, for example, in DE 10 2012 104 045 A1. Essential components of such scroll compressors are two scroll parts (scrolls) that can be moved relative to one another. The scroll parts are usually designed as a stationary, fixed scroll (fix scroll, displacement scroll) and as a movable, orbiting scroll (counter scroll, rotor scroll). The two scrolls have basically the same structure and each have a base plate (main body, scroll disk) and a spiral (snail-shaped) wall (spiral wall, scroll wall) extending in the axial direction from the base plate. In the assembled state, the spiral walls of the two scrolls are nested in one another and form several compression chambers between the scroll walls that touch in sections.

An orbiting movement is to be understood here and in the following in particular as an eccentric, circular movement path in which the movable scroll itself does not rotate about its own axis.

When the movable scroll orbits, the sucked-in gas-oil mixture travels via an inlet from a low-pressure chamber to a first, radially outer compression chamber (suction chamber) and from there via further compression chambers (compression chamber) to the radially innermost compression chamber (discharge chamber) and from there over a central outlet, for example in the form of a bore, and optionally two adjacent auxiliary valves, also in the form of bores in the base plate of the fixed scroll, into an outlet or high-pressure chamber. The chamber volume in the compression chambers decreases from radially outside to radially inside, and the pressure of the increasingly compressing medium increases. During operation of the scroll compressor, the pressure in the compressor chambers thus increases from radially outside to radially inside.

With increasing load in the compressor, the surface pressure between the two scroll parts in the scroll center, i.e. in the area of the discharge chambers, also increases. Here and in the following, surface pressure means the force per contact area between the scrolls, in particular between the spiral tips of the spiral walls and the respectively opposite base plate, ie the compressive stress between the scrolls. In contrast to pressure, the surface pressure is not isotropic, which means that the surface pressure is direction-dependent is, and is not necessarily constant over the contact area. Due to the higher surface pressure in the radially inner area of the spiral walls, the robustness and service life of the scroll compressor is disadvantageously reduced.

To counteract this stress in the scroll center, a relief contour with a tangential transition is applied to a spiral wall, for example. DE 10 2017 110 759 A1, for example, provides a relief ramp in the form of a conical section of a spiral end area of the spiral wall, which connects the radially innermost compressor chamber formed by the spiral end areas of the scroll spirals with the outlet rather than would be the case without a gate. This allows the compressed fluid to flow out of the outlet when it reaches a discharge pressure so that compression does not result in undesirable over-pressure in the compression chamber.

The invention is based on the object of specifying a particularly suitable scroll compressor for refrigerants in a vehicle air conditioning system. In particular, a more even surface pressure between the two scrolls should be realized. The invention is also based on the object of specifying a particularly suitable electric refrigerant drive with such a scroll compressor.

With regard to the scroll compressor, the object is achieved with the features of claim 1 and with regard to the refrigerant drive with the features of claim 10. Advantageous refinements and developments are the subject of the dependent claims. The advantages and configurations listed with regard to the scroll compressor can also be transferred to the refrigerant drive and vice versa.

The scroll compressor according to the invention is provided for compressing a refrigerant of a vehicle air conditioning system and is suitable and set up for this.

The scroll compressor has two scrolls that can be moved in opposite directions. Both

Scrolls can be rotating scrolls, so-called co-rotating scrolls. Co-Rotating Scrolls), in which both scrolls are driven around an eccentric axis. However, the scrolls are preferably designed as a fixed scroll and as a movable scroll, which means in the driven state—ie in operation (compressor operation)—orbiting (oscillating) scroll. The movable scroll is also referred to below as an orbiting scroll. The following explanations for movable and fixed scrolls also apply accordingly to rotating scrolls.

The scrolls or scroll parts each have a base plate (bottom plate) and a spiral wall (scroll spiral) extending essentially perpendicularly therefrom, with the particularly crescent-shaped compressor chambers being formed between the interlocking spiral walls of the two scrolls (scroll parts). The spiral walls of the scroll parts, which are preferably of essentially symmetrical design, each have a spiral angle of approximately 720°, for example.

The spiral walls of the scrolls each have an axial contact surface, referred to as a spiral tip (scroll tip), for contact with the respective other base plate. According to the invention, one of the spiral walls has a spiral end region which is drawn in axially opposite the respective spiral tip. As a result, a particularly suitable scroll compressor is realized.

In the following, the compression chambers are also divided into suction chambers, compression chambers and discharge chambers. There is an even number of suction and compression chambers for symmetrical scrolls. Symmetrical means here that both spiral lengths, ie the length of the spiral walls of the fixed and orbiting scrolls, are essentially of the same length, ie that the spiral walls have essentially the same spiral angle.

The suction chambers are open to a low-pressure side (suction side). Once the suction chambers are closed off by the orbiting movement of the scrolls, they become compression chambers whose crescent-shaped volume men is successively compressed or reduced in the course of the orbiting movement towards the center of the spiral. The two radially innermost compression chambers are referred to here as discharge chambers. The discharge chambers connect or unite (merge) in a process also known as "merging" to form a common discharge chamber, which conveys the compressed refrigerant out of the discharge chamber via the discharge opening.

Here and in the following, the spiral end regions mean in particular the central or radially inner regions of the spiral walls, between which the outlet chamber is formed in the course of the compression process.

Due to the axial offset of the spiral end area, at least a partial interruption of the bearing of the spiral tip on the opposite base plate is realized. In other words, at least one tangential connection is realized between the outlet chamber and an adjacent discharge or compression chamber. Due to the resulting fluidic and pressure-technical coupling between the compression chambers, an undesired overpressure within the central outlet chamber is avoided, as a result of which the surface pressure in the center of the spiral is reduced and distributed to the outside. This distributes the surface pressure more evenly, avoiding or at least reducing local stresses inside or in the center of the scroll compressor. As a result, the wear on the scrolls is reduced and their service life and robustness are improved.

“Axial” or an “axial direction” is understood here and in the following in particular as a direction parallel (coaxial) to the axis of rotation of the scroll compressor, ie perpendicular to the base plates. Correspondingly, here and in the following, “radial” or a “radial direction” is understood to mean, in particular, a direction oriented perpendicularly (transversely) to the axis of rotation of the scroll compressor along a radius of the scrolls. Here and in the following, “tangential” or a “tangential direction” means in particular a direction along the circumference of the scrolls (circumferential direction, azimuthal direction), ie a direction perpendicular to the axial direction and to the radial direction. In an advantageous embodiment, the spiral end area is drawn in axially opposite the spiral tip over the entire width of the spiral wall. This means that the spiral end region as a whole is offset or retracted with respect to the spiral tip. As a result, in addition to a tangential connection, a radial connection is also realized between the outlet chamber and adjacent ejection or compression chambers, as a result of which a particularly reliable reduction in the surface pressure in the center of the spiral is made possible.

In a preferred embodiment, a transition area oriented along the course of the spiral is provided, by means of which the spiral end area is drawn in axially relative to the spiral tip. In this case, the transition area has a contour or course along the course of the spiral which is adapted to the desired surface pressure. For example, the transition area has a stepped profile.

In a suitable development, the transition area has a continuous and monotonous course with regard to the spiral course. Such curves are associated with greater manufacturing effort, but allow a particularly uniform surface pressure in the course of the compaction process. In this case, the transition region has, for example, an approximately parabolic or quadratic profile.

In a design that is particularly simple in terms of design, the transition area along the course of the spiral is designed as a straight ramp. The transition area is thus designed as a relief ramp for the spiral tip.

The beginning or the length of the spiral end area or the transition area is preferably determined experimentally by means of pre-characterization for the respective scroll compressor. In an expedient embodiment, the spiral end area and/or the transition area begins at a point on the spiral wall which, in the area of the radially innermost compression chamber, i.e. the (scroll) outlet chamber, rests against the other spiral wall in each case when innermost compression compression chamber has the smallest volume during the compression process. In other words, the spiral end area begins in the area of the contact point of the spiral walls at the time of separation, at which the outlet chamber is dissolved and at which the two discharge chambers merge into a new common discharge chamber. This point is also referred to below as the seal-off point.

In a suitable development, the spiral end area or the transition area is produced by machining the spiral wall, in particular by means of milling.

An additional or further aspect of the invention provides that the axial shoulder or offset of the spiral end area relative to the spiral tip has an axial height of between 0.005 mm (millimeters) and 0.025 mm, in particular approximately

0.01 mm, preferably about 0.015 mm. This means that the axial height difference between the beginning and the end of the transition area is between 0.005 mm and 0.025 mm.

The term "approximately" refers in particular to a certain length range around the specified value, for example ±0.005 mm. For example, a height of about 0.01 is to be understood as (0.01±0.005) mm, ie as a length range between 0.0095 mm and 0.015 mm.

In one possible embodiment, the spiral wall of the movable or orbiting scroll is provided with the spiral end area.

The refrigerant drive according to the invention is designed in particular as a refrigerant compressor, for example as an electromotive scroll refrigerant compressor, of a motor vehicle. The refrigerant drive is provided here in particular for compressing a refrigerant of a motor vehicle air conditioning system, and is suitable and set up for this. The refrigerant drive has an electric motor drive, which is controlled and/or regulated by power electronics. The drive is drivingly coupled to a compressor head, where in which the compressor head is designed as a scroll compressor as described above. As a result, a particularly suitable refrigerant drive is realized.

Exemplary embodiments of the invention are explained in more detail below with reference to a drawing. Show in it:

1 a perspective view of a refrigerant drive,

Fig. 2 in a perspective view of a section of a movable

refrigerant drive scroll,

Fig. 3 in plan view, in detail, the movable scroll and a fixed scroll,

4 shows the movable scroll in a sectional view,

5 shows a sectional view of a detail of the movable scroll, and

6 to 9 in schematic side view different versions of a transition area of the movable scroll.

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

1 shows a refrigerant drive 2 according to the invention, which is installed, for example, in a refrigerant circuit, not shown in detail, of an air conditioning system of a motor vehicle. The electric motor refrigerant compressor 2 has an electric (electric motor) drive 4 and a scroll compressor 6 coupled to it as a compressor head. A bearing plate (center plate) 8 is provided as a mechanical interface between the drive 4 and the compressor head 6 , by means of which the scroll compressor 6 is connected to the drive 4 in terms of drive technology.

The bearing plate 8 forms an intermediate wall between a drive housing 10 and a compressor housing 12. The scroll compressor 6 is connected (joined, screwed) to the drive 4 by means of flange connections 14 distributed on the circumference and extending in an axial direction A of the refrigerant drive 2, which are only shown in the figures are provided with reference symbols by way of example. A compressor-side housing section of the drive housing 10 is designed as a motor housing for accommodating an electric motor, not shown in detail, and on the one hand through an integrated housing partition wall (not shown) to an electronics housing provided with a housing cover with motor electronics (electronics) 16 that control the electric motor, and on the other hand through the center plate 8 closed. In the area of the electronics housing, the drive housing 10 has a connection section 18 for making electrical contact between the electronics 16 and an on-board network of the motor vehicle.

The refrigerant drive 2 has a (refrigerant) inlet or (refrigerant) feed 20 for connection to the refrigerant circuit and a (refrigerant) outlet 22 . The inlet 20 is formed in an area of the motor housing that faces the electronics housing. The outlet 22 is formed on a bottom of a compressor head housing 12 . When connected, the inlet 20 forms the low-pressure or suction side (suction gas side) and the outlet 22 forms the high-pressure or pump side (pump side) of the refrigerant drive 2.

The scroll compressor 2 has two scrolls 24, 26 (FIG. 3) which can be moved in relation to one another or in relation to one another and which are arranged inside the compressor housing 12.

The scroll 24 shown in more detail in FIGS. 2, 4 and 5 is driven in an orbiting manner when the scroll compressor 6 is in operation. The scroll 26 is rigid, that is to say fixed to the housing, in the compressor housing 12 . The two scrolls (scroll parts) 24, 26 mesh with their helical or spiral spiral walls (scroll walls, scroll spirals) 24a, 26a, which protrude axially from a respective base plate 24b, 26b. A number of compressor chambers 28 are formed between the scrolls 24, 26, only the radially innermost outlet chamber being provided with a reference number in FIG. In the area of the outlet chamber 28 , the base plate 26b of the scroll 26 has a central, high-pressure-side opening as an outlet 30 , via which the compressed refrigerant is guided into a high-pressure chamber of the scroll compressor 6 . Between the scroll 26 and the high-pressure chamber, that is to say on the bottom of the base plate 26b, a reed valve (finger spring valve) is arranged, for example, as a covering or closing part, with which the outlet 30 is covered. A reed valve is to be understood here in particular as a non-return valve which, without any other external drive, opens in the flow direction solely due to pressure differences on the two valve sides and closes again automatically, ie covers the outlet 30 .

The spiral wall 24a of the scroll 24 has an axial contact surface for contact with the base plate 26b, which is also referred to below as the spiral tip (scroll tip) 24c. Spiral wall 24a has a central spiral end portion 32 which is indented axially opposite spiral tip 24c. The spiral end area 32 has a transition area 34 and an end area 36 .

The transition area 34 and the spiral end area 32 are produced by machining the spiral wall 24, in particular by means of milling. In this case, the transition area 34 is designed in particular as a relief ramp for the radially innermost compression chamber 28, so that the surface pressure in the scroll center is reduced.

FIG. 4 shows a sectional view of the scroll 24, with FIG. 5 showing a section V of FIG. 4 on an enlarged scale. In FIG. 4 two points A and B of the spiral tip 24c are marked, which are shown in FIG. 2 correspondingly.

The end region 36 is arranged at the radially inner spiral end of the spiral wall 24a and is oriented parallel to the base plate 24b. As can be seen in particular in FIG. 5, the end region 36 is drawn in by means of an axial height 38 in relation to the spiral tip 24c. The height 38, ie the height or axial offset between the end area 36 and the spiral tip 24c, is realized by means of the transition area 34. The spiral end area 32 or the transition area 34 extend over the entire width of the spiral wall. in a With a suitable dimensioning, the height 38 is dimensioned, for example, at about 0.015 mm.

The transition region 34 has a beginning 40 opening into the spiral tip 24c and an end 42 opening into the end region 36 (FIG. 2, FIG. 5). In an alternative embodiment that is not shown in detail, the transition region 34 can also extend over the entire spiral end region 32 so that the end 42 is essentially arranged at the spiral end, with the spiral end region 32 essentially having no end region 36 .

The beginning 40 of the scroll end region 32 or the transition region 34 is preferably determined experimentally for the scroll compressor 2 by means of pre-characterization. In this case, the beginning 40 is arranged, for example, in the area of a seal-off point. This means that the beginning 40 is in particular at a point on the spiral wall 24a which, in the region of the (scroll) outlet chamber 28, rests against the respective other spiral wall 26a when the outlet chamber 28 has the smallest volume. In other words, the spiral end area 32 or the transition area 34 begins in the area of the contact point of the spiral walls 24a, 26a at the point in time when the compressed fluid is expelled from the outlet chamber 28 or at the point in time of separation.

The position of the beginning 40 is explained in more detail below with reference to FIG. 3 in relation to a spiral wall geometry.

The spiral wall 24a is designed as two involutes of a circle that are offset relative to one another, which form the inside and outside 44, 46 of the spiral wall 24a. The involutes of a circle or the inner and outer sides 44, 46 are connected to one another via two circular arcs 48, 50 with different radii of curvature at the end of the spiral. The end of the spiral shown in more detail in FIG. 3 merges from the inside or inner contour 44 of the spiral wall 24a into a convex circular arc 48 with a comparatively large radius. The convex circular arc 48 is converted into the outside or outer contour 46 via a concave circular arc 50 with a comparatively small radius. The beginning 40 is here arranged at the point on the spiral wall 24c at which the inner contour 44 merges into the circular arc 48 .

The transition region 34 has a contour or course along the course of the spiral which is adapted to the desired surface pressure. Different courses of the transition region 34 are explained in more detail below with reference to the schematic and simplified representations of FIGS.

In the embodiments of FIGS. 6, 7 and 9, the transition area 34 has a continuous and monotonous profile. The transition region 34 in the exemplary embodiment in FIG. 8 is stepped and discontinuous.

6 shows an embodiment as a linear ramp with a constant slope. This essentially corresponds to the embodiment of the transition area 24 shown in Fig. 2 and Fig. 3 and Fig. 4.

In the embodiments of FIGS. 7 and 9 , the transition region 24 has an approximately square or parabolic shape, with the concave shape merging into a convex shape towards the end 42 in the embodiment of FIG. 9 .

The invention is not limited to the exemplary embodiments described above. On the contrary, other variants of the invention can also be derived from this by a person skilled in the art without departing from the subject matter of the invention. In particular, all of the individual features described in connection with the exemplary embodiments can also be combined with one another in other ways without departing from the subject matter of the invention.

It is thus possible, for example, to introduce the spiral end region 32 accordingly into the spiral tip of the spiral wall 26a. reference list

2 refrigerant drive

4 drive

6 scroll compressors

8 end shield

10 drive housing

12 compressor housing

14 flange connection

16 engine electronics

18 connection section

20 admission

22 outlet

24, 26scrolls

24a, 26a spiral wall

24b, 26b base plate

24c spiral tip

28 compression chamber/discharge chamber

30 outlet

32 Spiral End Section

34 transition area

36 end area

38 height

40 beginning

42 end

44 inside/inner contour

46 outside/outer contour

48, 50 arcs

A axial direction

V neckline

A, B point

Claims

Claims Scroll compressor (6) for refrigerants of a vehicle air conditioning system, having

- Two scrolls (24, 26) that can be moved relative to one another, each with a base plate (24b, 26b) and each with a spiral wall (24a, 26a), the spiral walls (24a, 26a) intermeshing and forming compression chambers (28),

- wherein the spiral walls (24a) have a spiral tip (24c) as an axial contact surface on the respective other base plate (26b),

- wherein one of the spiral walls (24a) has a spiral end region (32) which is constricted axially opposite the respective spiral tip (24a). Scroll compressor (6) according to claim 1, characterized in that the spiral end area (32) is drawn in axially over the entire width of the spiral wall. Scroll compressor (6) according to Claim 1 or 2, characterized in that a transition region (34) oriented along the course of the spiral is provided, over which the spiral end region (32) is drawn in axially relative to the spiral tip (24c). Scroll compressor (6) according to Claim 3, characterized in that the transition region (34) has a continuous and monotonous course with regard to the spiral course. Scroll compressor (6) according to Claim 3 or 4, characterized in that the transition region (34) is designed as a straight ramp along the course of the spiral. Scroll compressor (6) according to one of claims 1 to 5, characterized in that the scroll end region (32) or the transition region (34) begins at a point on the scroll wall (24a) which in the region of the radially innermost compressor chamber (28) at the other Spiral wall (26) rests when the radially innermost compression chamber (28) has the smallest volume in the course of the compression process. Scroll compressor (6) according to one of Claims 1 to 6, characterized in that the spiral end region (32) or the transition region (34) is produced by machining the spiral wall (24a) by machining. Scroll compressor (6) according to one of Claims 1 to 7, characterized in that the axial offset between the spiral tip (24c) and the spiral end region (32) has an axial height of between 0.005 mm and 0.025 mm, in particular approximately 0.01 mm. Scroll compressor (6) according to any one of claims 1 to 8, characterized in that the scroll wall (24a) of a movable scroll (24) is provided with the scroll end portion (32). Electric refrigerant drive (2) of a motor vehicle, having an electric motor drive (4) and a scroll compressor (6) coupled thereto according to one of Claims 1 to 9 as the compressor head.