EP3670915B1 - Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour un climatisateur de véhicule - Google Patents

Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour un climatisateur de véhicule Download PDF

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Publication number
EP3670915B1
EP3670915B1 EP19191561.0A EP19191561A EP3670915B1 EP 3670915 B1 EP3670915 B1 EP 3670915B1 EP 19191561 A EP19191561 A EP 19191561A EP 3670915 B1 EP3670915 B1 EP 3670915B1
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EP
European Patent Office
Prior art keywords
scroll
compressor
pressure
pressure chamber
duct
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EP19191561.0A
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German (de)
English (en)
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EP3670915A1 (fr
Inventor
Dennis RYMA
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Brose Fahrzeugteile SE and Co KG
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Brose Fahrzeugteile SE and Co KG
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Priority to EP19191561.0A priority Critical patent/EP3670915B1/fr
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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
    • F04C18/0246—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
    • F04C18/0292—Ports or channels located in the wrap
    • 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
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid
    • 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
    • F04C29/0021—Systems for the equilibration of forces acting on the pump

Definitions

  • the invention is in the field of 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 DE 10 2017 110 913 B3 known.
  • 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 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 or compressor, where the refrigerant then releases the heat it has absorbed via a heat exchanger 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.
  • the resulting gas-oil mixture is separated, with the separated gas being introduced into the air conditioning circuit, while the separated oil can be fed to the scroll compressor as a suitably electric motor-driven refrigerant compressor for lubricating moving parts.
  • Such a scroll compressor for the refrigerant or the refrigerant-oil mixture of a motor vehicle air conditioning system is, for example, in 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-preasure or counter-pressure mechanism in a scroll compressor (scroll compressor) is given 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 , described.
  • Essential components of the scroll compressor are a fixed scroll (fixed scroll) and a movable, orbiting scroll (movable, orbiting scroll).
  • the two scrolls are basically constructed in the same way and each have a base plate and a spiral-shaped wall (wrap) extending in the axial direction starting from the base plate. In the assembled state, the spiral walls of the two scrolls lie within one another and form several compression chambers between the scroll walls that touch one another in sections.
  • the sucked-in gas-oil mixture reaches a first, radially outer compression chamber via an inlet 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 auxiliary valves in the form of also bores in the base plate of the fixed scroll into a discharge 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.
  • the central gas-oil outlet (and each of the auxiliary valves or orifices, if applicable) is on the baseplate rear of the fixed scroll through a Spring valve closed.
  • the spring valve opens as a result of the pressure difference between the compression chambers and the high-pressure chamber. If necessary, after the spring valve has been triggered, the compressed gas-oil mixture flows into the high-pressure chamber of the scroll compressor (on the back of the fixed scroll) where it is separated into oil and gas. Then, when the pressure in the compression chambers opposite the high-pressure chamber has dropped accordingly, the spring valve closes automatically.
  • the two scrolls are pressed apart due to the pressure generated in the compressor chambers and the resulting axial force, so that a gap and thus leaks can arise between the compressor chambers.
  • the orbiting scroll is pressed against the fixed scroll - if necessary in addition to an oil film between the friction surfaces of the two scrolls.
  • the corresponding axial force (counterforce) is generated by providing a pressure chamber (back pressure chamber) on the back of the base plate of the orbiting scroll, in which a specific pressure is generated.
  • the pressure in the back-pressure chamber in the known scroll compressor increases to, for example, approx. 6 bar to approx. 9 bar at a pressure ratio of, for example, 3 bar (low pressure) to 25 bar (high pressure).
  • the medium-pressure channel is positioned at approximately 405°, starting from the start of the scroll spiral (spiral wall) of the movable (orbiting) scroll.
  • FIG. 12 shows a range of the relative compressor chamber volume in which the back-pressure port (with different port diameters) should be open (fluid-connected). This range is between 55% and approx. 100% of the (relative) chamber volume.
  • a (relative) pressure drop or pressure increase by a factor of 2 can be seen in the volume range under consideration.
  • the opening starting value of the back pressure port is therefore approximately 100% or approximately 95% of the relative compressor chamber volume.
  • a spiral compressor with a housing in which a fixed scroll with a base plate and a spiral formed thereon and a movable scroll revolving around an axis of rotation, also with a base plate and a spiral formed thereon, are arranged.
  • a discharge chamber (high pressure chamber) is formed between the base plate of the fixed scroll and a housing portion.
  • a bearing partition with a shaft bearing located in the housing delimits a suction or inlet chamber and forms with the base plate of the moving scroll a back pressure chamber (backpressure chamber) which communicates with the compression chamber between the scrolls via a delivery channel in the moving scroll.
  • the delivery chamber and the back pressure chamber communicate via a secondary delivery passage that extends generally axially through an outer wall of the fixed scroll.
  • the secondary supply passage supplies oil or refrigerant gas separated in the discharge chamber by an oil separator into the back pressure chamber to restore the pressure in the back pressure chamber after a pressure drop in a short time.
  • a scroll compressor with a support body, with which one of the scrolls can be supported on one side is known.
  • the scroll compressor has an infeed cylinder with which the support body can be acted upon in such a way that it keeps the scrolls in contact with one another, the support body being guided with a guide so that it cannot be tilted substantially.
  • the supporting body is guided transversely to an axis in a floating manner relative to the housing.
  • the invention is based on the object of specifying a particularly suitable scroll compressor, in particular one that is or can be driven by an electric motor, as a refrigerant compressor for a vehicle air conditioning system. Leakages should also be reduced as much as possible and friction losses between the fixed scroll and the orbiting scroll should be avoided or at least kept as minimal as possible.
  • the scroll compressor In a housing with a high-pressure chamber and with compression chambers and with a back-pressure chamber, the scroll compressor has a fixed scroll and a movable, ie in the driven state—ie in operation (compressor operation)—orbiting (oscillating) scroll.
  • the scrolls or scroll parts each have a base plate and a spiral wall, the compressor chambers being formed between the intermeshing spiral walls of the two scrolls (scroll parts).
  • the base plate of the fixed scroll defines the high pressure chamber and the base plate of the movable scroll defines the back pressure chamber.
  • the counter-pressure chamber is connected to at least one of the compression chambers via a pressure line that runs at least partially in the fixed scroll.
  • the pressure line is connected via a first channel to at least one of the compression chambers and also via a second channel to the high-pressure chamber.
  • a static pressure that also acts in the back-pressure chamber is created in the pressure line, via which the back-pressure chamber communicates in terms of flow with the high-pressure chamber and with the at least one compression chamber.
  • the scroll compressor is intended and set up in particular for refrigerants in a vehicle air conditioning system.
  • the first channel is located in the base plate of the fixed scroll.
  • the second channel is arranged in or formed by a filter (filter insert) which is inserted in the high-pressure chamber in a bore opening which is made in the base plate on the high-pressure chamber plate side and there by a positioning and retaining collar for the filter -Insert is surrounded.
  • the pressure line expediently has at least a first line section, which is arranged in the base plate of the fixed scroll, and a second line section which is connected to the first line section and is arranged in a boundary wall of the fixed scroll.
  • the boundary wall can be part of the fixed scroll or the housing.
  • first line sections running obliquely are provided starting from the borehole opening in the base plate of the fixed scroll.
  • One of these first line sections runs to the second line section in the boundary wall and opens into it.
  • the other of these first line sections runs to the first channel, ie within the base plate of the fixed scroll towards the (selected) position of the first channel.
  • the counter-pressure chamber is separated from a low-pressure chamber by means of an intermediate wall.
  • a (third) line section of the pressure line leading to the back pressure chamber is arranged in this intermediate wall, which suitably serves as an end shield for a shaft driving the movable scroll.
  • This line section can in turn be designed in a simple manner as a radial bore in the intermediate wall.
  • this line section of the pressure line is designed as a groove in the intermediate wall in connection with a plate (wear plate) covering it.
  • the cross-sectional area of the pressure line is at least a factor of two (2) larger than the cross-sectional area of the first passage connected to the compression chamber and the second passage connected to the high-pressure chamber.
  • the cross-sectional area of the first channel connected to the compression chamber is advantageously in turn larger than the cross-sectional area of the second channel connected to the high-pressure chamber.
  • the ratio between the cross-sectional area of the first passage connected to the compression chamber and the cross-sectional area of the second passage connected to the high-pressure chamber is between 3 (three) and 5 (five), preferably 4 (four).
  • the cross-sectional areas of the two channels should expediently be as small as possible.
  • the cross-sectional area of the first duct connected to the compression chamber is expediently between 0.03 mm 2 and 1.5 mm 2 , preferably 0.2 mm 2 .
  • the cross-sectional area of the second channel connected to the high-pressure chamber is expediently between 0.008 mm 2 and 0.2 mm 2 , preferably 0.05 mm 2 .
  • the diameter of the first channel should be between 0.2 mm and 1 mm, preferably 0.5 mm, and that of the second channel should be between 0.1 mm and 0.5 mm, preferably 0.25 mm.
  • the first and/or the second channel are designed as a bore which opens into the pressure line. Because of the low Wall thickness (wall thickness) of the base plate of the fixed scroll in the area of the two channels, the respective bore or the respective channel thus acts as an orifice or throttle.
  • This flow control and an effective adaptive adjustment of the pressure in the counter-pressure chamber to different operating points of the scroll compressor (in cooling or heat pump mode) is supported or can be further improved by the fact that the first channel connected to the compressor chamber - based on a relative chamber volume of about 100% in the radially outermost compressor chamber and a rotation or shaft angle of 0° - is fully open at a rotation or shaft angle of (63.5 ⁇ 5.5)° and up to a rotation or shaft angle of ( 343.5 ⁇ 5.5)° remains open. This corresponds to a relative volume change in the compressor chamber volume from (91.15 ⁇ 0.75)° to (23.0 ⁇ 0.3)°.
  • the radial distances between the two channels and a central outlet which is arranged in the fixed base plate and leads into the high-pressure chamber are suitably of different sizes, so that the operating channels are deliberately not arranged directly (axially) opposite one another.
  • the radial distance between the second channel leading into the high-pressure chamber can be larger or smaller than the radial distance between the first channel, which is connected to the compression chamber, and the central outlet.
  • the two flow-regulating channels in their connection with the pressure line in the fixed scroll allow an effective and self-adjusting adjustment of the pressure in the counter-pressure chamber to the respective operating point of the scroll compressor without additional flow-regulating components for flow throttling, such as valves, nozzles, throttles or other channels, bores or orifices.
  • Adaptive control of the pressure in the back pressure chamber is done by means of the two channels and the pressure line in the fixed scroll at a pressure ratio between suction pressure (low pressure) and high pressure of 5 (at a suction pressure of 3 bar and a high pressure of 15 bar) just as reliably self-adjusting as with a pressure ratio of about 8 (at a suction pressure of 3 bar and a high pressure of 25 bar) or 10 (at a suction pressure of 1.5 bar and a high pressure of 15 bar) for the refrigerant R-134A (working point when operating as a heat pump).
  • this two-channel pressure line system in the fixed scroll can be used to achieve high process stability for series production.
  • the two channels in the stationary scroll are subject to virtually the same conditions during the course of a scroll coating, for example a paint coating, so that tolerances that can lead to fluctuations in the back pressure level cancel each other out (reduce).
  • the scroll compressor can be operated with high efficiency at operating points in cooling and heat pump mode, in particular because leakage can be reduced and friction losses between the scroll parts can be kept to a minimum.
  • the self-adjusting pressure in the back pressure chamber causes the effective axial force due to the adaptive adjustment not to be larger than the sum of the axial forces in the compression chambers, or always only a small amount, in which different pressures typically prevail during compressor operation.
  • the particularly effective flow control and adaptive adjustment of the pressure in the counter-pressure chamber to different operating points of the scroll compressor is advantageously determined or influenced by the specified cross-sectional ratios of the pressure line and the two channels and their positioning in relation to the compressor chamber(s).
  • the positioning is suitably selected in such a way that in particular the first channel opens at a relative volume of the compression chamber (compression chamber volume) of approx. 90% and remains open in the course of a relative pressure change up to a relative volume of the compression chamber of approx. 23% before the respective channel during the orbiting movement of the orbiting scroll is covered or overlapped by its spiral wall and is connected (overlapping) to a compressor chamber lying radially further outwards.
  • the first channel connecting the compression chamber with the penstock should be positioned in the fixed scroll at an angle (spiral angle ⁇ ) of 350° to 390°, especially 370°, this angle ⁇ starting from both the beginning and the end the spiral wall (scroll spiral) of the fixed scroll can be measured (applied).
  • the two axially spaced channels can be arranged at mutually different radial and/or azimuthal positions.
  • the inside 1 Refrigerant compressor 1 shown is installed in a refrigerant circuit, not shown, of an air conditioning system of a motor vehicle.
  • the electric motor refrigerant compressor 1 has an electric (electric motor) drive module 2 and a compressor module coupled to it in the form of a scroll compressor 3 .
  • the scroll compressor 3 is connected in drive terms to the drive module 2 via a mechanical interface 4 formed between the drive module 2 and the scroll compressor 3 .
  • the mechanical interface 4 serves as a bearing plate on the drive side and forms an intermediate wall 5 (FIGS. 2 and 3).
  • the scroll compressor 3 is connected (joined, screwed) to the drive module 2 by means of flange connections 6 distributed on the circumference and extending in the axial direction A of the refrigerant compressor 1 .
  • a partial housing area of a drive housing 7 of the refrigerant compressor 1 is designed as a motor housing 7a for accommodating an electric motor 13 ( 2 ) formed and on the one hand by an integrated housing partition 7b ( 2 ) to an electronics housing 7d provided with a housing cover 7c with motor electronics (electronics) 8 controlling the electric motor 13 and on the other hand closed by the mechanical interface 4 with the end shield and the intermediate wall 5 .
  • the drive housing 7 has a connection section 9 with motor connections 9a and 9b routed to the electronics 8 for electrically contacting the electronics 8 to an on-board network of the motor vehicle.
  • the drive housing 7 has a refrigerant inlet or refrigerant feed 10 for connection to the refrigerant circuit and a refrigerant outlet 11 .
  • the outlet 11 is formed on the bottom of a compressor housing 12 of the scroll compressor 3 .
  • the inlet 10 forms the low-pressure or suction side (suction gas side) and the outlet 11 forms the high-pressure or pump side (pump side) of the refrigerant compressor 1.
  • FIG. 2 shows schematically the electric motor refrigerant compressor 1 in a sectional view along a rotation axis 14 of the electric motor 13, which is a brushless direct current motor (BLDC) and has a cylindrical rotor 15. This is surrounded on the circumference by a hollow-cylindrical stator 16 .
  • the rotor 15 comprises a number of permanent magnets and is rotatably mounted about the axis of rotation 14 by means of a shaft 17 .
  • the stator 16 has a number of electrical coils, which are energized by means of the electronics 8, which in turn is connected, for example, to a bus system and the on-board network of the motor vehicle.
  • the electronics 8 are arranged in the electronics housing 7d of the drive housing 7, which is separated from the stator 16 and the rotor 15 by means of the intermediate wall 5.
  • the housing cover 7c which is detachably attached to the electronics housing 7d by means of screws, closes an access opening in the electronics housing 7b.
  • the motor electronics 8 has printed circuit boards 18, 19 which are arranged one above the other in the axial direction A.
  • a bridge circuit of the printed circuit board 18, which is closest to the intermediate housing wall 7b, is in contact with the electrical coils of the stator 16 via energizing lines 19, which are routed through the intermediate housing wall 7b.
  • the bridge circuit is fed by the vehicle electrical system and controlled by a control circuit on the other printed circuit board 19, which is connected to the bus system in terms of signals.
  • the scroll compressor 3 has a movable scroll (scroll part) 21 arranged in the compressor housing 12 .
  • This is coupled via an eccentric shaft journal 17a with, for example, two joining pins, of which only one joining journal 17b is visible, to the shaft 17 of the electric motor 13, which is guided into the mechanical interface 4 with the A-side end shield.
  • the eccentric shaft journal 17a is mounted in a roller or ball bearing 22a held in the movable scroll 21.
  • Another rolling or ball bearing 22b supporting the shaft 17 is in the mechanical interface 4 serving as the A-side end shield and there in the Partition 5 arranged.
  • the movable scroll (scroll part) 21 is orbitally driven in operation of the scroll compressor 3 .
  • the scroll compressor 3 also has a fixed scroll (scroll part) 23 rigidly fastened in the compressor housing 12 .
  • the two scrolls (scroll parts) 21, 23 mesh with their snail or spiral scroll walls (scroll spirals) 21a, 23a, which protrude axially from a respective base plate 21b, 23b.
  • Compressor chambers 24 are formed between their scroll walls or scroll spirals 21a, 23a and the base plates 21b, 23b, the volume of which is changed when the electric motor 13 is in operation.
  • a counter-pressure chamber (back-pressure chamber) 25 in the intermediate wall 5.
  • This is in the compressor housing 12, referred to simply as the housing below, from the base plate 21b of the movable scroll 21 and/or from an intermediate plate (wear plate) 5a ( 3 ) limited in the form of a steel plate, which has good sliding properties for the orbiting scroll 21.
  • the back pressure chamber 25 partially extends into the base plate 21b of the movable scroll 21 .
  • the coolant is introduced through the inlet 10 into the drive housing 7 and there into the motor housing 7a.
  • This area of the drive housing 7 forms the suction or low-pressure side 26.
  • the intermediate wall 7b of the housing prevents the coolant from penetrating into the electronics housing 7d.
  • the refrigerant is mixed with oil present in the refrigerant circuit and passed along the rotor 15 and the stator 16 through an opening (or several openings, 3 ) 27 in the intermediate wall 5 to the scroll compressor 3.
  • the mixture of refrigerant and oil is compressed by means of the scroll compressor 3, with the oil serving to lubricate the two scrolls 21, 23, so that friction is reduced and consequently efficiency is increased.
  • the oil also serves as a seal in order to prevent the coolant located between the two scrolls (scroll parts) 21, 23 from escaping in an uncontrolled manner.
  • the compressed refrigerant and oil mixture is directed into a high pressure chamber 29 within the compressor housing 12 via a central outlet 28 in the base plate 23b of the fixed scroll 23 .
  • an oil separator (cyclone separator) 30 In the high-pressure chamber 29 there is an oil separator (cyclone separator) 30. Inside the oil separator 30, the mixture of refrigerant and oil is set in a rotary motion, with the heavier oil due to increased inertia and increased mass being directed to the walls of the oil separator 30 and in a lower portion of the oil separator 30 while the refrigerant is discharged upward or sideways through the outlet 11.
  • the high pressure chamber 29 is defined within the housing 12 by the base plate 23b of the fixed scroll 23.
  • the central outlet 28 into the high pressure or discharge chamber 29, which is located in the radially innermost chamber region 24' of the compression chambers 24, is drilled into the base plate 23b of the fixed scroll 23.
  • the central outlet 28 is closed with a spring valve (finger spring valve) 33 as long as the pressure in the compressor chambers 24 is lower than the pressure in the high-pressure chamber 29. If the pressure of the compressed refrigerant-oil mixture in the compressor chambers 24, in particular in the central chamber region 24', is greater than the pressure in the high-pressure chamber 29, the spring valve 33 opens more or less automatically.
  • a stop element 34 which is fixed in the high-pressure chamber 29 to the fixed scroll 23, for example to its base plate 23b, limits the stroke of the spring valve 33.
  • the spring valve 33 closes the outlet 28 again automatically due to its spring preload. In this way, the compressed refrigerant-oil mixture - depending on the speed of the shaft 17 or depending on the operating point of the scroll compressor 3 - passes continuously (continuously) or intermittently or pulsating via the central outlet 28 from the compression chamber 24 into the high-pressure chamber 29.
  • a pressure line 35 is provided in the stationary scroll 23 , via which the compression chambers 24 and the high-pressure chamber 29 communicate with the counter-pressure chamber 25 in terms of flow.
  • the pressure line 35 is connected via a first channel 36 to the compressor chambers 24 formed between the scroll walls 21a, 23a and via a second channel 37 to the high-pressure chamber 29 in an area which, during operation, essentially contains the refrigerant and only a small amount of oil having.
  • FIG. 4 shows schematically in a block diagram the fluidic or pressure-carrying connection of the counter-pressure chamber 25 via the pressure line 35 and the two channels 36, 37, which act as orifices or throttles, on the one hand with the high-pressure chamber 29 and on the other hand with the compressor chambers 24.
  • the in the base plate 23b of the fixed scroll 23, for example as a bore, is provided with the reference numeral 36, as is its diaphragm or throttle symbol.
  • This is fluidically connected via the suction gas opening 27 to the compressor chambers 24 of the scroll compressor 3 , as illustrated by the broken arrow line 40 .
  • the pressure line 35 is made up of a first line section 35a, which is introduced into the base plate 23b of the fixed scroll 23, suitably as a radially running bore, and a second line section 35b, which is suitably made as an axially running bore in a cup-shaped boundary wall 23c of the fixed scroll 23 is arranged.
  • the second line section 35b can also be introduced into the (axial) housing wall of the compressor housing 12 .
  • the bores or line sections 35a, 35b open into one another within the base plate 23b or merge into one another.
  • the entrance opening of the radial bore of the first Line section 35a is closed on the periphery of the boundary wall 23c in a manner not shown.
  • the counter-pressure chamber 25 is separated from the suction or low-pressure chamber 26 by means of the intermediate wall 5 .
  • the intermediate wall 5 which accommodates the bearing 22a and 22b for the shaft journal 17a and the shaft 17 as an end shield, a third line section 35c of the pressure line 35 leading to the counter-pressure chamber 25 is arranged.
  • This line section 35c can be designed analogously as a radially running bore in the intermediate wall 5 .
  • the third line section 35c in the intermediate wall (interface) 5 can be designed as a groove which is open toward the orbiting scroll 21 and is closed by the intermediate plate (ware plate) 5a.
  • the cross-sectional area of the pressure line 35 is many times, for example ten times smaller than the cross-sectional area of the central outlet 28. However, the cross-sectional area of the pressure line 35 is many times larger than the cross-sectional area of the two channels 36 and 37. In addition, the cross-sectional area of the with the compression chambers 24 connected to the first duct 36 is larger than the cross-sectional area of the second duct 37 connected to the high-pressure chamber 29.
  • the diameter of the central outlet 28 is between 5mm and 10mm.
  • the diameter of the pressure line 35 is between 1 mm and 10 mm.
  • the diameter of the first channel 36 is 0.5 mm, for example, and the diameter of the second channel 37 is 0.25 mm, for example, each with a circular bore or channel cross section.
  • the first channel 36 and the second channel 37 are designed as bores and (in terms of flow) act as an orifice plate or throttle. With this, from the pressure line 35 and the two channels 36, 37 formed channel system a particularly effective flow control of the (static) pressure in the back pressure chamber 25 is achieved.
  • the radial distance of the first channel 36 connected to the compression chambers 24 to the base plate 23b of the fixed Scrolls 23 arranged and leading into the high-pressure chamber 29 central outlet 28 is greater in the exemplary embodiment than the radial distance of the second channel 37 connected to the high-pressure chamber 29 to the central outlet 28.
  • the second channel 37 can also be arranged closer to the central outlet 28 than the first channel 36. It is essential that the two channels 36 and 37 are not arranged directly axially opposite one another.
  • the Figures 5 and 6 show a perspective representation or a top view of the fixed scroll 23 with the first channel 36, which is arranged in the base plate 23b at a predetermined angular position P K1 within the scroll wall (scroll spiral) 23a and there to the pressure line 35, i.e. to its inside first line section 35a running along the base plate 23b.
  • the channel exit of the second line section 35b, which opens into the third line section 35c, within the boundary wall 23c of the fixed scroll 23, which is preferably closed all the way around, can also be seen.
  • the Figures 7 and 8 show a perspective representation or a plan view of the fixed scroll 23 with a view of its plate side of the base plate 23b located in the high-pressure chamber 29.
  • a filter (filter insert) 42 is received in this receiving opening 41, which has a filter shaft 42a and an orifice or throttle head 42b, in which the second channel 37, for example as a central bore , is provided.
  • the opening 41 is surrounded in the manner of a collar by a wall 43 for receiving, positioning and/or stabilizing the position of the screen or throttle head 42b of the filter (filter insert) 42 .
  • the first line section 35a of the pressure line 35 is formed by two sections a 1 , a 2 in the form of oblique bores which are made in the base plate 23b from the receiving opening 41 .
  • the first section a 1 runs in the direction of the center or the central region of the base plate 23b.
  • the second section a 2 runs to the second line section 35b of the pressure line 35 in the boundary wall 35c of the fixed scroll 23 and opens there into the second line section 35b of the pressure line 35.
  • the first channel opens into the first section a 1 of the first line section 35a of the pressure line 35 36 with the production of the (pressure and/or flow) connection of the compression chambers 24 with the pressure line 35 and via this with the in figure 9 counter-pressure chamber 25, not shown.
  • the two flow-regulating channels 36, 37 and their connection to the pressure line 35 leading into the counter-pressure chamber 25 in the fixed scroll 23 achieve a particularly effective, self-adjusting adjustment of the pressure in the counter-pressure chamber 25 in practically all working areas or points of the scroll compressor 3 .
  • the adaptive control of the pressure in the counter-pressure chamber 25 by means of the two channels 36, 37 and the pressure line 35 in the fixed scroll 23 is just as reliable and self-adjusting at a suction pressure (low pressure) of 3 bar and a high pressure of 15 bar. as with a suction pressure of 3 bar and a high pressure of 25 bar or a suction pressure of 1.5 bar and a high pressure of 15 bar (working point in heat pump operation).
  • the scroll compressor 3 and thus the refrigerant compressor 1 can therefore be operated with high efficiency at operating points in the cooling mode and in the heat pump mode of a vehicle air conditioning system.
  • the flow control and adaptive adjustment of the pressure in the counter-pressure chamber 25, also at different operating points of the scroll compressor 3, can be influenced by the cross-sectional ratios of the pressure line 35 and the two channels 36, 37 and their positioning in relation to the compressor chamber(s) 24.
  • the position P K1 , P K2 of the first channel 36 is selected such that it opens at a relative volume of the compressor chamber 24 of approximately 90% and remains open up to a relative chamber volume of approximately 25%.
  • the scroll compressor 3 which is provided and set up in particular for refrigerants of a vehicle air conditioning system, has in a compressor housing 12 with a high-pressure chamber 27 and with compressor chambers 24 as well as with a counter-pressure chamber (back-pressure chamber) 25, a fixed scroll 23 and a movable scroll 23 that orbits (oscillates) during compressor operation , performing a rolling motion) Scroll 21 up.
  • the scrolls 21, 23, which each have a base plate 21a, 23a and a scroll or spiral wall 21a integral with this (formed onto it), form the compressor chamber(s) 24 between their intermeshing scroll or spiral walls 21a or 23a .
  • the base plate 23b of the fixed scroll 23 defines the high-pressure chamber 27, and the base plate 21b of the movable scroll 21 defines the back-pressure chamber 25.
  • the counter-pressure chamber 25 is connected to at least one of the compression chambers 24 via a pressure line 35 running at least partially in the fixed scroll 23 and a first channel 36 and to the high-pressure chamber 27 via a second channel 37 . Due to the operation, a static pressure is created or prevails in the pressure line 35, via which the counter-pressure chamber 25 communicates fluidically with the high-pressure chamber 27 and with the at least one of the compressor chambers 24, and also acts in the counter-pressure chamber 25.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Claims (14)

  1. Compresseur à spirales (3) pour réfrigérant d'un système de climatisation de véhicule, présentant
    - un boîtier (12) avec une chambre à haute pression (29) et avec des chambres de compression (24) ainsi qu'avec une chambre de contre-pression (25),
    - une spirale fixe (23) avec une plaque de base (23b) et avec une paroi de spirale (23a), la plaque de base (23b) de la spirale fixe (23) délimitant la chambre à haute pression (29),
    - une spirale mobile (21) avec une plaque de base (21b) et avec une paroi de spirale (21a) qui s'engage dans la paroi de spirale (23b) de la spirale fixe (23) et forme avec celle-ci les chambres de compression (24), la plaque de base (21b) de la spirale mobile (21) délimitant la chambre de contre-pression (25),
    - la chambre de contre-pression (25) étant reliée par l'intermédiaire d'une conduite sous pression (35) aux chambres de compression (24) et à la chambre à haute pression (29),
    - la conduite sous pression (35) s'étendant au moins partiellement dans la spirale fixe (23) et étant reliée par l'intermédiaire d'un premier canal (36) à au moins une des chambres de compression (24) ainsi que par l'intermédiaire d'un deuxième canal (37) à la chambre à haute pression (29), et
    - le deuxième canal (37) étant agencé dans un filtre (42) qui est inséré dans une ouverture de réception (41) qui est ménagée dans la plaque de base (23b) de la spirale fixe (23) sur son côté de plaque tourné vers la chambre à haute pression (29).
  2. Compresseur à spirales (3) selon la revendication 1, caractérisé en ce qu'à partir de l'ouverture de réception (41), deux sections s'étendant en oblique (a1, a2) de la ou d'une première section de conduite (35a) de la conduite sous pression (35) sont prévues, le premier canal (36) débouchant dans une première section (a1) et la deuxième section (a2) débouchant dans la ou dans une deuxième section de conduite (35b) de la conduite sous pression (35).
  3. Compresseur à spirales (3) selon la revendication 1 ou 2, caractérisé en ce que le premier canal (36) qui est relié à l'au moins une des chambres de compression (24) et/ou le deuxième canal (37) relié à la chambre à haute pression (29) est ou sont agencé (s) dans la plaque de base (23b) de la spirale fixe (23).
  4. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 3, caractérisé
    - en ce que la conduite sous pression (35) présente une première section de conduite (35a) qui est agencée dans la plaque de base (23b) de la spirale fixe (23), et
    - en ce que la conduite sous pression (35) présente une deuxième section de conduite (35b) reliée à la première section de conduite (35a) et agencée dans une paroi de délimitation (23c) de la spirale fixe (23) ou dans une paroi de boîtier du boîtier (12).
  5. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la chambre de contre-pression (25) est délimitée par rapport à une chambre à basse pression (26) au moyen d'une paroi intermédiaire (5) dans laquelle est agencée une troisième section de conduite (35c) de la conduite sous pression (35) menant à la chambre de contre-pression (25), notamment réalisée sous forme d'alésage ou de rainure.
  6. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le rapport entre la surface de section transversale de la conduite sous pression (35) et la surface de section transversale du premier canal (36) relié à la chambre de compression (24) est compris entre 10 et 100, de préférence entre 15 et 70.
  7. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le rapport entre la surface de section transversale de la conduite sous pression (35) et la surface de section transversale du deuxième canal (36) relié à la chambre à haute pression (29) est compris entre 50 et 500.
  8. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 7, caractérisé en ce que la surface de section transversale du premier canal (36) relié à la chambre de compression (24) est supérieure à la surface de section transversale du deuxième canal (37) relié à la chambre à haute pression (29).
  9. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la surface de section transversale du premier canal (36) relié à la chambre de compression (24) est comprise entre 0,03 mm2 et 1,5 mm2, de préférence 0,2 mm2.
  10. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 9, caractérisé en ce que la surface de section transversale du deuxième canal (37) relié à la chambre à haute pression (29) est comprise entre 0,008 mm2 et 0,2 mm2, de préférence 0,05 mm2.
  11. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 10, caractérisé en ce que le rapport entre la surface de section transversale du premier canal (36) relié à la chambre de compression (24) et la surface de section transversale du deuxième canal (37) relié à la chambre à haute pression (29) est compris entre 3 et 5, de préférence 4.
  12. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 11, caractérisé en ce que le premier canal (36) et/ou le deuxième canal (37) est ou sont réalisé(s) sous forme d'alésage et/ou agit(ssent) comme un diaphragme ou un étranglement.
  13. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 12, caractérisé
    - en ce que la spirale orbitale (21) parcourt une plage angulaire de 900° depuis le processus de compression dans les chambres de compression (24) jusqu'au processus d'éjection dans la chambre à haute pression (29) par l'intermédiaire d'une sortie centrale (28), et
    - en ce que le premier canal (36) relié à la chambre de compression (24) est agencé à partir du début radialement extérieur ou de l'extrémité radialement intérieure de la paroi de spirale (23a) de la spirale fixe (23) à un angle de spirale (ϕ1,2) de 350° à 390°, de préférence 370°.
  14. Compresseur à spirales (3) selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la distance radiale entre le premier canal (36) relié à la chambre de compression (24) et une sortie centrale (28) agencée dans la plaque de base (23b) de la spirale fixe (23) et menant dans la chambre à haute pression (29) est supérieure ou inférieure à la distance radiale entre le deuxième canal (37) relié à la chambre à haute pression (29) et la sortie centrale (28).
EP19191561.0A 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour un climatisateur de véhicule Active EP3670915B1 (fr)

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EP19191561.0A EP3670915B1 (fr) 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour un climatisateur de véhicule

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EP18212076.6A EP3667086B1 (fr) 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour une installation de climatisation de véhicule
EP19191561.0A EP3670915B1 (fr) 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour un climatisateur de véhicule

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EP18212076.6A Division EP3667086B1 (fr) 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour une installation de climatisation de véhicule
EP18212076.6A Division-Into EP3667086B1 (fr) 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour une installation de climatisation de véhicule

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EP19191561.0A Active EP3670915B1 (fr) 2018-12-12 2018-12-12 Machine volumétrique selon le principe de la spirale, en particulier compresseur à spirale pour un climatisateur de véhicule

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JP3146963B2 (ja) * 1995-12-27 2001-03-19 ダイキン工業株式会社 スクロール形流体機械
DE19720790A1 (de) * 1997-05-17 1998-12-03 Bitzer Kuehlmaschinenbau Gmbh Kompressor
DE19853240A1 (de) * 1998-11-18 2000-05-31 Bitzer Kuehlmaschinenbau Gmbh Kompressor
JP5315933B2 (ja) * 2008-06-05 2013-10-16 株式会社豊田自動織機 電動スクロール型圧縮機
JP5201113B2 (ja) 2008-12-03 2013-06-05 株式会社豊田自動織機 スクロール型圧縮機
JP5199951B2 (ja) * 2009-06-01 2013-05-15 日立アプライアンス株式会社 スクロール圧縮機
KR101810461B1 (ko) * 2011-03-24 2017-12-19 엘지전자 주식회사 스크롤 압축기
DE102012104045A1 (de) 2012-05-09 2013-11-14 Halla Visteon Climate Control Corporation 95 Kältemittelscrollverdichter für Kraftfahrzeugklimaanlagen
DE102017110913B3 (de) 2017-05-19 2018-08-23 OET GmbH Verdrängermaschine nach dem Spiralprinzip, Verfahren zum Betreiben einer Verdrängermaschine, Fahrzeugklimaanlage und Fahrzeug

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CN113167273B (zh) 2023-06-27
CN113167273A (zh) 2021-07-23
EP3667086B1 (fr) 2023-03-29
EP3667086A1 (fr) 2020-06-17
WO2020120659A1 (fr) 2020-06-18

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