KR20180092829A - Refrigerant-scroll compressor for use within a heat pump - Google Patents

Refrigerant-scroll compressor for use within a heat pump Download PDF

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Publication number
KR20180092829A
KR20180092829A KR1020180003094A KR20180003094A KR20180092829A KR 20180092829 A KR20180092829 A KR 20180092829A KR 1020180003094 A KR1020180003094 A KR 1020180003094A KR 20180003094 A KR20180003094 A KR 20180003094A KR 20180092829 A KR20180092829 A KR 20180092829A
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South Korea
Prior art keywords
refrigerant
scroll compressor
chamber
helical
compressor
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KR1020180003094A
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Korean (ko)
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KR101953616B1 (en
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필립보 코잘라
토마스 클로텐
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한온시스템 주식회사
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0253—Details concerning the base
    • F04C18/0261—Details of the ports, e.g. location, number, geometry
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0246—Details concerning the involute wraps or their base, e.g. geometry
    • F04C18/0269—Details concerning the involute wraps
    • F04C18/0284—Details of the wrap tips
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F04C29/124—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps
    • F04C29/126—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type
    • F04C29/128—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet with inlet and outlet valves specially adapted for rotary or oscillating piston pumps of the non-return type of the elastic type, e.g. reed valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/261—Carbon dioxide (CO2)

Abstract

The present invention relates to a refrigerant scroll compressor (1) to be used inside a heat pump, capable of being operated at high efficiency. According to the present invention, the refrigerant scroll compressor to be used inside a heat pump comprises: a compressor housing (2); two spiral parts (3, 7) crossing and engaged with each other inside the compressor housing (2); a suction pressure chamber (80) to suck a refrigerant distributed to inner and outer suction chambers (8.1, 8.2); an intermediate compression chamber (9) divided into inner and outer intermediate compression chambers (9.1, 9.2); a refrigerant discharge chamber (10) allowing two inner end areas (3a, 7a) of the spiral parts (3, 7) to face each other therein; two or more refrigerant pre-outlets (4.1, 4.2) disposed on the front wall (2a) of the compression housing (2); one or more valves (6) for opening/closing the two or more refrigerant pre-outlets (4.1, 4.2); and a main refrigerant outlet (5) disposed on the front wall (2a) of the compression housing (2).

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a refrigerant scroll compressor for use in a heat pump,

The present invention relates to a refrigerant scroll compressor for use inside a heat pump comprising CO 2 as a refrigerant. The invention also relates to the use of said refrigerant scroll compressor for use in a refrigerant circulation system comprising CO 2 as refrigerant capable of operating in A / C mode and / or heat pump mode. The application field of the invention is, in particular, motor vehicle refrigerant compressors.

The concept of a scroll compressor is a compressor type name commonly used in terminology, also known as a drive worm compressor, a spiral compressor, or a spiral compressor. The scroll compressor operates according to the positive displacement principle. The scroll compressor is composed of two helical parts which are staggered and engaged with each other, wherein one helical part is stationary and the other helical part moves eccentrically on a circular path. At this time, the spiral portions maintain a minimum gap therebetween and form compression chambers which are continuously reduced in each revolution. As a result, the gas to be pumped is sucked from the outside, compressed in the compression chambers inside the scroll compressor, and discharged through the connection at the center of the spiral portion.

The refrigerant scroll compressor for air conditioner refrigerant circulation which is currently in use is designed to operate at high efficiency in A / C mode. The purpose of such a design is to have as low a power consumption as possible simultaneously with a high refrigerant mass flow. This results in a lower outlet temperature at a given pressure and speed.

In a heat pump circulation system, it is necessary to reach a high outlet temperature to heat the passenger compartment. In this case, a scroll compressor with the maximum efficiency in a high pressure situation is required to reach a high outlet temperature. At relatively high pressures, the isentropic efficiency is reduced, resulting in the compressor operating relatively less efficiently. In addition, the bearing load also increases.

Conventional scroll compressors with a wrap angle in the range of 440 ° to 900 ° require two pre-outlets and one main outlet for efficient operation. When the pressure in the compression chamber falls below the high pressure, each outlet is closed by a valve. This prevents the hot gas from flowing back into the compression chamber and reducing the efficiency of the compressor. To this end, the air conditioner compressor generally has three outlet valves, a so-called three finger valve.

When the air conditioner compressor is configured to operate efficiently in the A / C mode condition, such a compressor is often associated with the drawback that it operates significantly less efficiently in the heat pump mode situation. Thus, for scroll compressors operating in heat pump mode and requiring high outlet temperatures, it is highly desirable that the high pressure gas flow back into the compression chamber.

JP 2002-070765 A describes a scroll compressor with a bypass mechanism, wherein the scroll compressor is used to prevent overpressure in the scroll compressor. The bypass mechanism assumes an open spiral structure with a large dead volume at the scroll center. In this case, only a low compression ratio can be achieved because of the open scroll structure at the center of the scroll as described above. Therefore, a high pressure state with a high compression ratio, i.e. a compression ratio of high pressure / suction pressure > 3.7, is not possible in the heat pump mode situation.

It is an object of the present invention to provide a scroll compressor that operates at high efficiency in A / C mode as well as in heat pump mode.

The above object is achieved by a refrigerant scroll compressor having the features of claim 1. Improvements are set forth in the dependent claims.

The refrigerant scroll compressor according to the present invention is suitable for use in a heat pump including CO 2 as a refrigerant. A refrigerant scroll compressor for use inside a heat pump comprising CO 2 as a refrigerant

- compressor housing,

Two helical portions meshingly engaged with each other inside the compressor housing wherein one helical portion is fixed and the other helical portion is movable eccentrically on a circular path so that the helical portion is movable between the helical portions The volume of the plurality of different compression chambers formed is changed to cyclic wherein the individual helical portions have a total wrap angle in the range of 440 ° to 900 °, preferably 580 ° to 700 °, respectively, The following compression chambers are formed between the parts:

A compression chamber as a suction pressure chamber for sucking refrigerant divided into an inner suction chamber and an outer suction chamber in accordance with the position of the individual suction chamber in relation to the movable spiral portion,

An intermediate compression chamber connected to the suction pressure chamber and divided into an internal intermediate compression chamber and an external intermediate compression chamber, depending on the position of the individual suction chamber in relation to the movable spiral portion,

A refrigerant discharge chamber in communication with said at least one intermediate compression chamber in which two inner end regions of said spiral portions face,

Two or more refrigerant pre-outlets in the front wall of the compressor housing facing the spirals,

One or more pre-outlet valves for opening and closing the two refrigerant dictionary outlets and

- a refrigerant main outlet (always open and not provided with a valve) in the front wall of the compressor housing in the center of the stationary spiral, facing the spirals.

The object of the present invention also relates to the use of the aforementioned refrigerant scroll compressor for use in a refrigerant circulation system comprising CO 2 as refrigerant which can operate as an A / C mode and / or a heat pump mode.

According to the formation of the refrigerant scroll compressor according to the present invention, high pressure is already achieved in the A / C mode condition before the refrigerant flows out through the main discharge opening. This eliminates the need for valves at the refrigerant main outlet. Particularly the shape of the spiral portions results in omitting the main outlet valve. In one particularly preferred embodiment of the invention, the individual spiral portions each have a total wrap angle of 660 [deg.]. Preferably, the helical portions are formed in relation to their helical structure to reduce the volume of the refrigerant discharge chambers insolublely to as much as 9% of the suction volume or displaced volume of the scroll compressor. In one particularly preferred embodiment, the helical portions are formed in relation to their helical structure to reduce the volume of the refrigerant discharge chambers to an insoluble volume corresponding to? 5.0% of the suction volume, for example 4.9% of the suction volume . When the suction volume is 6 cm 3, it will correspond to about 0.3 cm 3 of the insoluble volume.

In the heat pump mode, the refrigerant pre-outlets are kept mostly closed, and the entire refrigerant flows out through the refrigerant main outlet. In the low pressure state, backflow from the high pressure side deteriorates the compression and causes a high outlet temperature.

In one preferred embodiment of the invention, the bores of the refrigerant pre-outlets and the refrigerant main outlet are arranged essentially linearly and equally spaced from each other, in which case the main outlet is in the middle and the refrigerant pre- And is symmetrically disposed at the outlet. The intermediate compaction chamber is divided into two intermediate compaction chambers, which are preferably positioned symmetrically with respect to one another. In this case, one external compression chamber and one internal compression chamber are always made, depending on the position of the movable spiral portion. In other words, the external compression chamber abuts the convex side of the movable spiral portion, and the internal compression chamber abuts the concave side of the movable spiral portion. The bores of the refrigerant pre-outlets are at least temporarily located in the intermediate compression chamber area, in which case one or more bores are located in the outer compression chamber area and the same number of bores are located in the inner compression chamber area. Due to the linear and symmetrical arrangement of the refrigerant pre-outlets and the main outlet bore, the pre-outlet valves for the inner and outer compression chambers can be opened and closed together when the compression pressures are equal, and delivery to the refrigerant main outlet is ensured .

U-shaped or V-shaped valves are particularly suitable as the valves for opening and closing the two refrigerant outlet openings. U-shaped or V-shaped arms (U- or V-arms) And the one opened refrigerant main outlet is preferably positioned between the U-shaped or V-shaped arms.

A further advantage of the present invention is that the compressor can be operated in a heat pump mode at a low pressure and a relatively lower compressor rotational speed. This leads to improved NVH (Noise, Vibration, Harshness) values, which in turn reduces vibrations that can be heard or shaken in the vehicle and cause lower power consumption and bearing load, This further extends the useful life of the bearing and provides the possibility of reducing the bearing size. In addition, the required outlet valve is provided at a more economical cost.

Further details, features and advantages of embodiments of the present invention will be apparent from the following detailed description of embodiments with reference to the accompanying drawings. In the drawing:
Figure 1A shows a cut-out of a scroll compressor with a stationary spiral portion and refrigerant outlet bores in the front wall of the scroll compressor housing towards this spiral, as an internal view,
1b shows the front wall of the scroll compressor housing with refrigerant outlet bores as an exterior view,
Figure 2a shows a front wall of a prior art scroll compressor housing with three outlet bores and three finger valves,
Figure 2b shows the front wall of the scroll compressor housing with three outlet bores and two finger valves,
Figure 3 schematically shows the helical parts of a scroll compressor which are staggered with each other,
Figure 4a schematically shows the helical parts of a scroll compressor which are stitched together staggered at a crankshaft rotation angle of 0 ° / 360 °,
Figure 4b schematically shows the helical parts of the scroll compressor, which are staggered from each other at a crankshaft rotation angle of 90 °,
Figure 4c schematically shows the spiral parts of the scroll compressor, staggeredly engaged with each other at a crankshaft rotation angle of 180 °,
Figure 4d schematically shows the helical parts of the scroll compressor, staggered from each other at a crankshaft rotation angle of 270 °,
5 is a graph showing the isentropic pressure of the refrigerant according to the rotation angle of the crankshaft during isentropic compression in the refrigerant scroll compressor in the A / C mode, and
6 is a graph showing the isentropic pressure of the refrigerant according to the angle of rotation of the crankshaft during isentropic compression in the scroll compressor in the heat pump mode.

Figure 1a shows an internal view of a cut-out of a scroll compressor (1) having parts of a scroll compressor housing (2) to which a stationary spiral part (3) is fixed. In this case the part is the front wall 2a of the scroll compressor housing 2 facing the stationary spiral part. The stationary spiral portion (3) has an overall lap angle of 660 [deg.]. A scroll compressor with a wrap angle in the range of 440 [deg.] To 900 [deg.] Requires two pre-outlets (4.1; 4.2) and one main outlet (5) for efficient operation. According to figure la, two pre-outlets (4.1; 4.2) in the form of pre-outlet bores (4.1; 4.2) are located in the front wall (2a) of the scroll compressor housing (2) towards the stationary spiral part (3). The main outlet 5 in the form of a main outlet bore 5 is also arranged in the front wall 2a of the scroll compressor housing 2 towards the stationary spiral portion 3 in the center portion of the inner end region 3a of the stationary spiral portion, . In this case, the first pre-outlet bore 4.1 is formed between the first outlet bore 4.1 and the main outlet bore 5 without the wall of the stationary spiral part 3 being disposed between the first outlet bore 4.1 and the main outlet bore 5. [ The main outlet bore 5 is positioned in front of the inner side of the spiral portion 3 so as to be surrounded by the stationary spiral portion 3. The second pre-outlet bore 4.2 is located in front of the outer side of the stationary spiral section 3 such that the wall of the stationary spiral section 3 is disposed between the main outlet bore 5 and the second pre- Is set.

1b shows an external view of the scroll compressor 1 looking at the front wall 2a of the scroll compressor housing 2 with the pre-outlet bores 4.1 and 4.2 and the main outlet bore 5. [ In this case, the main outlet bore 5 is actually arranged in the middle of two pre-outlet bores 4.1, 4.2, wherein the main outlet bore 5 and the pre-outlet bore 4.1, 4.2, Respectively.

Figure 2a shows the front wall of a scroll compressor housing with three outlet bores and three finger valves as known in the prior art. Therefore, if the pressure in the compression chamber decreases to a range lower than the high-pressure range, all the outlets can be closed. Thereby preventing the high pressure gas from flowing back into the compression chamber and reducing the efficiency of the compressor.

Figure 2b shows a scroll similar to Figure 1b, looking at the front wall 2a of the scroll compressor housing 2, with the pre-outlet bores 4.1 and 4.2 and the main outlet bore 5, And shows an external view of the compressor (1). In this case, the main outlet bore 5 is actually arranged in the middle of the said outlet bores 4.1, 4.2, wherein the main outlet bore 5 and the pre-outlet bore 4.1, 4.2 are actually arranged linearly have. As a valve for opening and closing the two pre-outlet bores 4.1, 4.2, a U-shaped or V-shaped valve 6 is provided and the pre-outlet bores 4.1, 4.2 are U- or V- Can be simultaneously closed by the arms (6.1; 6.2), with one main outlet bore (5) being open in the free intermediate chamber between the U-shaped or V-shaped arms (6.1; 6.2). The valve may also be referred to as a two finger valve similar to a three finger valve.

Fig. 3 schematically shows a cross-section of a scroll compressor 1 with a stationary spiral 3 and a movable spiral 7 interlaced with each other. The two spiral portions each have a total wrap angle of 660 DEG by the entire wrap angle of the spiral portions. The movable spiral portion 7 can move eccentrically on the circular path and as a result the volume of the plurality of different compression chambers 8, 9, 10 formed between the spiral portions 3, 7 changes annularly. Since the total lap angle is 660 °, there are always three different types of compression chambers formed. As shown in Figure 3, the following compression chambers are formed:

- a suction pressure chamber (8) for suctioning the refrigerant, which is divided into an inner suction chamber (8.1) and an outer suction chamber (8.2) according to the position of the individual suction chambers (8.1, 8.2) An open / openable compression chamber,

Connected to said suction pressure chamber (8) and connected to said suction pressure chamber (8), consisting of one internal intermediate compression chamber (9.1) and an external intermediate compression chamber (9.2), always in accordance with the position of the movable spiral section The chamber 9,

- a refrigerant outlet chamber (10) connected to said intermediate compression chamber, in which two inner end regions (3a; 7a) of said spiral portions (3; 7) face.

Figure 3 schematically shows two refrigerant dictionary outlets (4.1; 4.2) in the front wall of the compressor housing, towards the spiral sections (3; 7). The two refrigerant outlet outlets (4.1; 4.2) may be closed by one or more pre-outlet valves. 3, the refrigerant main outlet 5 is located in the center of the stationary spiral portion 3, in the front wall of the compressor housing, towards the spiral portions 3, 7, The outlet is always open and does not have a valve.

Due to the special nature of the refrigerant (CO 2 ), the high pressure required at all A / C test points is achieved inside the intermediate pressure chambers (9.1, 9.2) when the angle of rotation is 360 °.

The helical structure given in particular from the wrap angle of the spiral portions 3, 7 of 660 ° respectively ensures that the insoluble volume which can be achieved amounts to ≤ 9%, preferably ≤ 5% of the suction volume or stroke volume. 3 shows the maximum compression position of the refrigerant discharge chambers 10 at the center of the spiral portion 3 (7).

The valve member at the main discharge port 5 does not negatively affect the output of the scroll compressor 1 when the high and low pressure ratio values in the suction chambers 8.1 and 8.2 are 3.7. This applies to all A / C mode situations.

When the pressure ratio is > 3.7, the absence of the valve at the main outlet 5 causes a refrigerant backflow into the compression chamber. This pressure ratio exists in the heat pump situation.

Figures 4a to 4d show a schematic view of the helical portions 3,7 of the refrigerant scroll compressor 1 which are staggeredly engaged with each other at various rotational angles of the crankshaft to which the movable spiral portion 7 is connected when in A / do. In this case, in the A / C mode, there is a maximum pressure of 3.7 between the high pressure of the refrigerant discharge chamber 10 and the low pressure of the suction chambers 8.1, 8.2.

Figure 4a shows a schematic view of the interlaced helical portions 3 (7) of the refrigerant scroll compressor 1 at a crankshaft rotation angle of 0 ° or 360 °. In this case, the internal pressure in the suction chambers (8.1, 8.2) reaches 35 bar. This internal pressure reaches 130 bar in both the intermediate compression chambers 9.1, 9.2 as well as in the refrigerant discharge chamber 10, respectively. In other words, the required high pressure is achieved in the intermediate compression chambers 9.1, 9.2 already in all test conditions of the air conditioner when the rotation angle is 360 °. Because of this, the main outlet 5 can be kept open and a valve is not required for this purpose. Only two refrigerant pre-outlets (4.1 and 4.2) are opened or closed by the pre-outlet valve.

Fig. 4b schematically shows the interlaced helical portions 3 (7) of the refrigerant scroll compressor 1 at a crankshaft rotation angle of 90 [deg.]. The internal pressures of the suction chambers 8.1, 8.2 reach 35 bar. The internal pressures of the intermediate compression chambers 9.1, 9.2 are 45 bar. The pressure in the refrigerant discharge chamber 10 reaches 130 bar.

Figure 4c shows a schematic view of the interlaced helical portions 3 (7) of the scroll compressor 1 at a crankshaft rotation angle of 180 °. In this case, the internal pressures of the suction chambers 8.1 and 8.2 reach 35 bar and the internal pressures of the intermediate compression chambers 9.1 and 9.2 rise to 57 bar. The pressure in the refrigerant discharge chamber 10 is-130 bar, with no variation.

Figure 4d includes a schematic view of the helical parts (3; 7) stitched together at a crankshaft rotation angle of 270 °. The internal pressures of the suction chambers 8.1, 8.2 reach 35 bar. The internal pressures of the intermediate compression chambers 9.1, 9.2 were increased to 79 bar. In addition, the pressure in the refrigerant discharge chamber (DC) is 130 bar.

As can be seen from the values mentioned in connection with Figs. 4A to 4D, in the A / C situation, the high pressure is already achieved before the refrigerant is discharged by the main outlet opening or the main outlet bore 5. This eliminates the need for valves at the refrigerant main outlet.

Fig. 5 shows the isentropic pressure of the refrigerant according to the rotation angle of the crankshaft in the isentropic compression in the refrigerant scroll compressor in the A / C mode, corresponding to Figs. 4A to 4D. The pressure of the inhaled refrigerant is 35 bar in the low pressure range (LP). The refrigerant is compressed while simultaneously reaching the pre-outlet bore region. The pressure of the refrigerant rises simultaneously with the rotation of the crankshaft and then finally reaches the high pressure level (HP), by which the refrigerant likewise reaches the main outlet bore area.

Pre-outlet valves are provided only for the pre-outlet bores, where the pre-outlet valves open and close the pre-outlets. Although there is no main discharge valve, there is no refrigerant backflow from the high pressure region to the combined internal compression chamber of the scroll compressor, because the compression chambers and the cavity next to the refrigerant main outlet are at the same pressure level . The refrigerant scroll compressor has a low outlet temperature in A / C mode.

6 is a graph showing the isentropic pressure of the refrigerant according to the angle of rotation of the crankshaft during isentropic compression in the scroll compressor in the heat pump mode.

The pressure of the inhaled refrigerant is firstly 20 bar in the low pressure range, and thus this pressure is significantly lower than in the A / C mode. The refrigerant is compressed and, at the same time, first reaches the pre-outlet bore region. The pressure of the refrigerant rises exponentially with the rotation of the crankshaft but is significantly lower than the high pressure level (HP) when the refrigerant reaches the refrigerant outlet bore region. This causes a reverse flow of refrigerant from the high pressure side into the combined internal compression chamber because the main outlet is always open and the compression chamber has a lower pressure level than the cavity next to the refrigerant outlet. The backflow of refrigerant into the combined internal compression chamber is schematically indicated by the vertical arrows in Fig. The reverse flow of the high temperature refrigerant gas is preferable in the heat pump mode, in which the high outlet temperature of the scroll compressor is sought.

1: Refrigerant scroll compressor
2: compressor housing
2a: front wall of the compressor housing
3: Fixed spiral part
3a: inner end region of the fixed spiral portion
4.1: Refrigerant pre-outlet, pre-outlet bore
4.2: Refrigerant pre-outlet, pre-outlet bore
5: Refrigerant main outlet, main outlet bore
6: Valve, pre-outlet valve
6.1: the first arm of the U-shaped or V-shaped valve (6)
6.2: Second arm of U-shaped or V-shaped valve (6)
7: Portable spiral part
7a: inner end area of the movable spiral part
8: suction pressure chamber, compression chamber
8.1: Internal suction chamber
8.2: External suction chamber
9: intermediate compression chamber
9.1: Internal intermediate compression chamber
9.2: External intermediate compression chamber
10: Refrigerant discharge chamber, compression chamber

Claims (8)

A refrigerant scroll compressor (1) for use inside a heat pump comprising CO 2 as a refrigerant, wherein the scroll compressor
The compressor housing (2),
Two helical parts (3; 7) staggeredly engaged with each other inside the compressor housing (2), wherein one helical part (3) of the two helical parts is stationary and the other helical part (7) So that the volume of the plurality of different compression chambers 8, 9, 10 formed between the spiral portions 3, 7 is changed to cyclic, and in this case, The spiral portions 3 and 7 each have a total wrap angle in the range of 440 ° to 900 ° and the following compression chambers 8, 9 and 10 are formed between the spiral portions:
- a suction chamber (8) for suctioning the refrigerant, which is divided into an inner suction chamber (8.1) and an outer suction chamber (8.2)
An intermediate compression chamber 9 divided into an internal intermediate compression chamber 9.1 and an external intermediate compression chamber 9.2,
- a refrigerant discharge chamber (10) in which two inner end regions (3a; 7a) of said helical portions (3; 7)
Two or more refrigerant pre-outlets (4.1; 4.2) in the front wall (2a) of the compressor housing (2) towards the helical parts (3; 7)
One or more valves (6) for opening and closing the two refrigerant dictionary outlets (4.1; 4.2) and
- a refrigerant main outlet (3) located in the center of the stationary spiral part (3) in the front wall (2a) of the compressor housing (2) towards the spiral parts (3; 7) and a refrigerant main outlet (5). The refrigerant scroll compressor (1) according to claim 1, characterized in that the individual spiral portions (3; 7) have a total wrap angle in the range of 580 ° to 700 °, respectively. 3. Refrigerant scroll compressor (1) according to claim 2, characterized in that said individual spiral portions (3; 7) each have a total wrap angle of 660 [deg.]. The scroll compressor (1) according to claim 1, characterized in that the spiral portions (3; 7) have a volume of refrigerant discharge chamber with a dead volume of ≤ 9% of the suction volume of the scroll compressor (1). The refrigerant scroll compressor (1) according to claim 1 or 2, The scroll compressor (1) according to claim 4, characterized in that said helical portions (3; 7) are formed in relation to its helical structure so as to reduce the volume of the refrigerant discharge chamber insolublely to ≤ 5% of the suction volume of said scroll compressor (1). ≪ / RTI > 2. A valve according to claim 1, characterized in that a U-shaped or V-shaped valve (6) is provided as a valve for opening and closing the two refrigerant pre-outlets (4.1; 4.2), the U- or V- 4.2 and 4.1 may be closed by the U-or V-arm (6.1; 6.2), and the one opened refrigerant main outlet (5) may be closed by the U- or V- ; 6.2). The refrigerant scroll compressor (1) according to claim 1 or 2, Use of a refrigerant scroll compressor (1) according to any one of claims 1 to 6 for use in a refrigerant circulation system comprising CO 2 as refrigerant, capable of operating in A / C mode and / or heat pump mode . 8. Use according to claim 7, characterized in that the refrigerant circulation system is operated in a heat pump mode and the refrigerant pre-outlets (4.1; 4.2) are kept mostly closed.
KR1020180003094A 2017-02-10 2018-01-10 Refrigerant-scroll compressor for use within a heat pump KR101953616B1 (en)

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DE102021203857A1 (en) 2021-04-19 2022-10-20 Robert Bosch Gesellschaft mit beschränkter Haftung Scroll compressor and method of operating the scroll compressor

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