EP1983191B1 - Kupplungsloser verdichter mit variabler verdrängung - Google Patents

Kupplungsloser verdichter mit variabler verdrängung Download PDF

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Publication number
EP1983191B1
EP1983191B1 EP07706626.4A EP07706626A EP1983191B1 EP 1983191 B1 EP1983191 B1 EP 1983191B1 EP 07706626 A EP07706626 A EP 07706626A EP 1983191 B1 EP1983191 B1 EP 1983191B1
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EP
European Patent Office
Prior art keywords
check valve
discharge
passage
housing portion
variable displacement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07706626.4A
Other languages
English (en)
French (fr)
Other versions
EP1983191A1 (de
EP1983191A4 (de
Inventor
Takeo Mizushima
Hiroyuki Ishida
Hiromichi Tanabe
Christian Marsais
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Thermal Systems Japan Corp
Original Assignee
Valeo Thermal Systems Japan Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Valeo Thermal Systems Japan Corp filed Critical Valeo Thermal Systems Japan Corp
Publication of EP1983191A1 publication Critical patent/EP1983191A1/de
Publication of EP1983191A4 publication Critical patent/EP1983191A4/de
Application granted granted Critical
Publication of EP1983191B1 publication Critical patent/EP1983191B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/1036—Component parts, details, e.g. sealings, lubrication
    • F04B27/1081—Casings, housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/0027—Pulsation and noise damping means
    • F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
    • F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1822—Valve-controlled fluid connection
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/14—Control
    • F04B27/16—Control of pumps with stationary cylinders
    • F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
    • F04B27/1804—Controlled by crankcase pressure
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1872—Discharge pressure

Definitions

  • the present invention relates to a variable displacement-type clutchless compressor according to the preamble of claim 1.
  • a clutchless compressor used in this type of application often includes a check valve with a predetermined valve opening pressure, disposed in an discharge passage in the compressor and forms a circulation path within the compressor (e.g., by opening the pressure control valve disposed on the gas supply passage for intake control) so as to circulate the refrigerant gas within the compressor in the air-conditioner OFF state.
  • patent reference literature 1 discloses a structure that includes a check valve 63 disposed at an exit area of an discharge muffler 44. Via the check valve 63 constituted with a valve element 67, a spring 68 and a spring seat 69, any reverse flow of liquid refrigerant from an external refrigerant circuit 37 to the discharge muffler 44 is prevented and also the compressed refrigerant gas is allowed to flow from the discharge muffler 44 into the external refrigerant circuit 37 (see paragraph 0035).
  • Patent reference literature 1 Japanese Unexamined Patent Publication No. H9-177671
  • a second variable displacement-type clutch compressor is shown in the US 5,871,337 A .
  • the check valve 63 located at the exit area of the discharge muffler 44 is accommodated inside the housing constituting the discharge muffler at a projecting portion of the housing that accommodates the check valve.
  • a high-pressure side piping of the external refrigerant circuit is connected to the projected portion in the structure disclosed in the publication. Since this necessitates the piping to be connected in a very limited space, reliable piping connection cannot always be assured. In other words, the structure gives rise to on-vehicle installation-related concerns.
  • Such concerns may be addressed by disposing the check valve in close proximity to a cylinder bore outer shell section so as to reduce the extent to which the housing portion to connect with the high-pressure side piping projects out.
  • the gap between the cylinder bore outer shell section and the check valve in this structure is bound to be very narrow, which, in turn, will increase the passage resistance.
  • a primary object of the present invention having been completed by addressing the issues discussed above, it is to provide a variable displacement-type clutchless compressor with which the extent to which the housing portion to connect with the high-pressure side piping connects projects out is minimized and an increase in the passage resistance is prevented by assuring a sufficient clearance between the cylinder bore outer shell section and the check valve.
  • variable displacement-type clutchless compressor according to claim 1.
  • the check valve and the discharge passage are disposed with an offset with the axial lines thereof shifted relative to each other and thus, the check valve is not disposed coaxially to the discharge passage connecting with the high-pressure side piping. Since this eliminates the need to dispose a check valve so as to project out at the muffler chamber in the vicinity of the cylinder bore outer shell section, the extent to which the housing portion where the discharge passage connecting with the high-pressure side piping is formed needs to project out can be minimized.
  • the check valve housing portion may include a space formed therein, which faces only the downstream-side end of the check valve (claim 2), so as to assure a smooth refrigerant flow by linearly supplying the refrigerant from the muffler chamber into the refrigerant circuit via the check valve housing portion, the communicating passage and the discharge passage without widening the refrigerant flow.
  • a space may be formed around the check valve in the check valve housing portion (claim 3) so as to ensure that oil adhering to the check valve does not hinder a release operation by collecting the oil returning from the refrigerating cycle around the check valve while the compressor is engaged in operation at the minimum discharge displacement.
  • the structure described above may include a safety valve communicating with the muffler chamber, which can be engaged in operation in correspondence to the pressure in the muffler chamber, so as to release the pressure in the discharge area if the pressure rises to an abnormally high level (claim 4), or a safety valve communicating with the discharge passage, which can be engaged in operation in correspondence to the pressure at the check valve downstream side (claim 5).
  • the safety valve may be disposed on a line extending from the communicating passage (claim 6).
  • the communicating passage and a safety valve mounting hole can be formed coaxially with each other, which facilitates machining and also allows the safety valve to close off the open end of the communicating passage, eliminating the need to provide a special blocking member.
  • variable displacement-type clutchless compressor described above may be a swash plate clutchless compressor, comprising a shaft passing through a crankcase and rotatably supported at the housing, a swash plate that rotates synchronously with the shaft and is disposed tiltably relative to the shaft, a piston held at a circumferential edge of the swash plate and engaged in reciprocal sliding motion inside the cylinder bore formed at the housing as the swash plate rotates and an suction area and an discharge area that selectively communicate with the cylinder bore as the piston slides reciprocally, in which the discharge displacement is controlled by adjusting the angle at which the swash plate is tilted (claim 7).
  • the variable displacement-type clutchless compressor may be a compressor other than a swash plate compressor.
  • the discharge area of the variable displacement-type clutchless compressor includes a muffler chamber, a check valve housing portion disposed downstream of the muffler chamber, an discharge passage connecting with the high-pressure side piping of the refrigerant circuit and formed substantially parallel to the check valve housing portion and a communicating passage communicating between the check valve housing portion on the check valve discharge side and the discharge passage.
  • FIG. 1 illustrates a swash plate compressor representing an example of a variable displacement-type clutchless compressor.
  • the compressor comprises a cylinder block 1, a rear head 3 attached onto the rear side (the right side in the figure) of the cylinder block 1 via a valve plate 2 and a front head 5 attached so as to close off the front side (the left side in the figure) of the cylinder block 1 and defining a crankcase 4.
  • the front head 5, the cylinder bore 1, the valve plate 2 and the rear head 3 are fastened together along the axial direction with fastening bolts 6.
  • the crankcase 4 defined by the front head 5 and the cylinder block 1 houses therein a drive shaft 7, one end of which projects out beyond the front head 5.
  • a drive pulley 10 rotatably fitted onto the outside of a boss portion 5a of the front head 5, is connected to the portion of the drive shaft 7 projecting out beyond the front head 5 via a relay member 9 mounted along the axial direction with a bolt 8, so as to communicate rotational motive power from the engine of the vehicle via a drive belt (not shown).
  • a space between the one end of the drive shaft 7 and the front head 5 is sealed with a high level of air tightness with a seal member 11 disposed between the drive shaft and the front head 5 and the one end of the drive shaft is rotatably supported at a radial bearing 12.
  • the other end of the drive shaft 7 is rotatably supported at a radial bearing 14 accommodated inside a recessed portion 13 formed at the cylinder block 1.
  • the recessed portion 13 where the radial bearing 14 is accommodated and a plurality of cylinder bores 15 disposed over equal intervals on the circumference of a circle centered on the recessed portion 13 are formed at the cylinder block 1, with a hollow single-ended piston 16 inserted in each cylinder bore 15 so as to slide reciprocally in the cylinder bore.
  • the thrust flange 17 is rotatably supported via a thrust bearing 18 so as to rotate freely relative to the inner surface of the front head 5, and a swash plate 20 is connected to the thrust flange 17 via a link member 19.
  • the swash plate 20 is tiltably disposed so that it tilts around a hinge ball 21 slidably disposed on the drive shaft 7, and rotates as one with the thrust flange 17 in synchronization with the rotation of the thrust flange 17 via the link member 19.
  • Engaging portions 16a of the single-ended pistons 16 are each held at the circumferential edge of the swash plate 20 via a pair of shoes 22.
  • the swash plate 20 also rotates.
  • the rotating motion of the swash plate 20 is then converted via the shoes 22 to reciprocal linear motion of the single-ended pistons 16 and, as a result, the volumetric capacity of a compression space 23 formed between the single-ended piston 16 inside each cylinder bore 15 and the valve plate 2 is altered.
  • An suction hole 31 and an discharge hole 32 are formed at the valve plate 2 in correspondence to each cylinder bore 15, whereas an suction chamber 33, where the working fluid to be supplied into the compression spaces 23 is stored and an discharge chamber 34, where the working fluid discharged from the compression space 23 is stored, are defined at the rear head 3.
  • the suction chamber 33 formed at a central area of the rear head 3, communicates with an suction passage (not shown) connecting with the discharge side of an evaporator and is also allowed to communicate with the compression spaces 23 via an suction hole 31 opened/closed via an suction valve 35.
  • the discharge chamber 34 formed around the suction chamber 33, is allowed to communicate with the compression space 23 via an discharge hole 32 opened/closed via an discharge valve 36.
  • the discharge displacement of the compressor is determined in correspondence to the stroke of the pistons 16, and the stroke of the pistons, in turn, is determined based upon the tilt angle of the swash plate 20 relative to a plane ranging perpendicular to the drive shaft 7.
  • the swash plate 20 is made to tilt with a specific angle at which the pressure difference between the pressure applied to the front surface of a piston 16, i.e., the pressure in the compression space 23 (the pressure inside the cylinder bore) and the pressure applied to the rear surface of the piston 16, i.e., the pressure in the crankcase 4 (the crankcase pressure Pc) and the level of force applied from a de-stroke spring 28, which applies a force to the hinge ball 21 along the piston stroke-reducing direction, are in balance with each other.
  • the discharge displacement is determined based upon the piston stroke determined in correspondence to the tilt of the swash plate 20.
  • a gas supply passage 40 ranging over the cylinder block 1, the valve plate 2 and the rear head 3 and communicating between the discharge chamber 34 and the crankcase 4 is formed with passage segments 1b, 2b and 3b.
  • a gas bleeding passage 41, communicating between the crankcase 4 and the suction chamber 33 is constituted with passage segments 1c and 2c formed at the cylinder block 1 and the valve plate 2, a passage 7c formed at the shaft 7 and the gap at the radial bearing 14.
  • Via a pressure control valve 42 disposed in the gas supply passage 40 the flow rate of the refrigerant flowing into the crankcase 4 are from the discharge chamber 34 is adjusted so as to control the pressure in the crankcase 4.
  • the gas supply passage 40 is opened via the pressure control valve 42 and an internal circulation path is formed inside the compressor with the compression space 23, the discharge hole 32, the discharge chamber 34, the gas supply passage 40, the crankcase 4, the gas bleeding passage 41, the suction chamber 33 and the suction hole 31.
  • the swash plate 20 assumes the smallest tilt angle or an angle close to the smallest tilt angle, the refrigerant gas is made to circulate inside the compressor through the internal circulation path instead of flowing out to the external circuit via the check valve to be detailed below. As the refrigerant gas circulates inside the compressor, the sliding portions inside the compressor.
  • the discharge chamber 34 communicates with a muffler chamber 37 formed at the circumferential edge of the cylinder block 1 via passage segments 2a and 1a formed at the valve plate 2 and the cylinder block 1.
  • the muffler chamber 37 is formed between the cylinder block 1 and a cover member 38 mounted at the outer circumference of the cylinder block 1.
  • a check valve housing portion 44 communicating with the muffler chamber 37 and housing the check valve 43 on the downstream side of the muffler chamber 37, an discharge passage 45 connecting with a high-pressure side piping of the refrigerant circuit and formed substantially parallel to the axial center of the check valve housing portion 44 with an offset relative to the axial center of the check valve housing portion 44 and a communicating passage 46 communicating between the check valve discharge side of the check valve housing portion 44 and the discharge passage 45 are formed.
  • the discharge chamber 34, the passage segments 1a and 2a, the muffler chamber 37, the check valve housing portion 44, the communicating passage 46 and the discharge passage 45 form an discharge area through which the refrigerant gas discharged from the compression space 23 is output to the outside of the compressor, whereas the suction chamber 33 and an suction passage (not shown) form an suction area through which the refrigerant is taken in from the outside of the compressor.
  • the front head 5, the cylinder block 1, the rear head 3 and the cover member 38 constitute the housing of the compressor.
  • the check valve 43 is accommodated inside the check valve housing portion 44, which does not project into the muffler chamber 37.
  • the check valve 43 may be, for instance, a valve disposed in Japanese Unexamined Patent Publication No. 2005-098155 , comprising a tubular case 51 with a solid bottom, a valve element 52 accommodated inside the case, a spring 53 that applies a force to the valve element 52 and a stopper 54 that regulates the movement of the valve element, as shown in FIG. 3 .
  • a valve hole 56 of the check valve is opened/closed as the valve element 52 moves onto or departs a seat surface 55 of the case 51.
  • the check valve housing portion 44 in the embodiment includes a space 47 which faces only the downstream-side end of the check valve 43. While the housing (cover member 38) projects out on the axial line of the check valve 43, the area where the discharge passage 45 connecting with the high-pressure side piping is formed does not project out anymore than the extent to which the check valve housing portion 44 projects out.
  • the communicating passage 46 is formed so as to extend from the inner wall surface of the cover member 38 through the discharge passage 45 to reach the space 47 located on the downstream side of the check valve 43, with an open end thereof closed off with a blocking member 48.
  • the refrigerant flowing out from the muffler chamber 37 via the check valve 43 then flows linearly through the space 47 facing opposite the downstream end of the check valve 43, the communicating passage 46 and the discharge passage 45 in sequence without widening the path of its flow, before being discharged into the high-pressure side piping.
  • a safety valve 49 communicating with the muffler chamber 37 which opens the muffler chamber to release the pressure therein when the pressure in the muffler chamber becomes equal to or higher than a predetermined level, is disposed at the cover member 38.
  • the check valve 43 included in the structure described above is accommodated inside the check valve housing portion 44 formed substantially parallel to the discharge passage 45 (the discharge passage 45 is not formed on the axial line of the check valve), the extent to which the portion of the housing where the discharge passage 45 connecting with the high-pressure side piping is present projects out is minimized so as to improve the installability in the vehicle by assuring ample piping connection space.
  • the check valve 43 is accommodated inside the check valve housing portion 44 so that it does not project into the muffler chamber 37, a sufficient clearance between the outer shell section of the cylinder bores 15 and the check valve 43 is secured (without reducing the passage section of the muffler chamber 37) whereby preventing an increase in the passage resistance.
  • the refrigerant flowing out of the muffler chamber 37 via the check valve 43 flows linearly to reach the discharge passage 45 without widening its path as it exits the check valve 43. It is then discharged into the high-pressure side piping. Thus, a smooth flow of the refrigerant discharged of the muffler chamber is assured.
  • FIG. 4 presents a variation of the structure described above. While the structure shown in FIG. 4 is similar to that described in reference to the previous example, in that the check valve 43 is accommodated inside the check valve housing portion 44 formed on the downstream side of the muffler chamber 37 so that the check valve does not project into the muffler chamber 37, that the safety valve 49 is disposed so as to communicate with the muffler chamber 37 and that the discharge passage 45 is disposed substantially parallel to the check valve housing portion 44 with an offset, instead of being disposed coaxially with the check valve housing portion 44, the check valve housing portion 44 in the variation is defined by the cover member 38 and a lid member 60 mounted from the outside of the cover member 38, with a space 61 formed at the check valve housing portion 44 to surround the check valve 43 and the space 61 connected to the discharge passage 45 via the communicating passage 46.
  • the communicating passage 46 in this structure is formed as a channel on the outer side of the cover member 38 via the check valve housing portion 44 while the lid member 60 is disengaged. It is to be noted that since other structural features are similar to those in the previous example, the same reference numerals are assigned to identical components so as to preclude the necessity for a repeated explanation thereof.
  • the check valve 43 is accommodated inside the check valve housing portion 44 formed substantially parallel to the discharge passage 45 without projecting into the muffler chamber 37 and thus, ample piping connection space is assured by minimizing the extent to which the housing projects out over the area where the discharge passage 45 is formed.
  • the passage resistance does not increase.
  • the space 61 is formed around the check valve 43, which makes it possible to collect the oil returning from the refrigerant circuit in the space around the check valve 43 when the compressor is engaged in operation at the smallest discharge displacement. As a result, smooth opening operation is enabled without any hindrance by oil adhering to the check valve 43.
  • FIG. 5 presents another structural example. While this structure is similar to that shown in FIG. 4 in that the check valve housing portion 44 is formed on the downstream side of the muffler chamber 37 to house the check valve 43 without the check valve projecting out into the muffler chamber 37, that the discharge passage 45 is formed to extend substantially parallel to the check valve housing portion 44 with an offset instead of being disposed coaxially with the check valve housing portion 44 and that the space 61 is formed around the check valve 43, the check valve housing portion 44 in this example is defined entirely by the cover member 38, the safety valve 49, communicating with the discharge passage 45, is engaged in operation in correspondence to the level of pressure on the downstream side of the check valve and the communicating passage 46 is formed so as to reach the space 61 through the discharge passage 45 from the inner wall surface of the cover member 38, with the open end of the communicating passage 46 closed off with a blocking member 48.
  • FIG. 6 presents yet another structural example. While the open end of the communicating passage 46 must be closed off with a blocking member 48 during formation of the communicating passage 46 or a lid member 60 must be disposed at the cover member 38 after machining the communicating passage 46 in the examples described earlier, the safety valve 49 communicating with the discharge passage 45 is disposed on a line extending from the communicating passage 46 and a mounting hole 62 at which the safety valve 49 is mounted and the communicating passage 46 are formed coaxially in this example.
  • the communicating passage 46 and the mounting hole 62 of the safety valve 49 are coaxial with each other, they can be formed at the same time, thereby facilitating the machining process.
  • the open end of the communicating passage 46 is closed off with the safety valve 49, no special blocking member is required, making it possible to minimize the number of required parts.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Claims (7)

  1. Kupplungsloser Kompressor mit variabler Verdrängung, mit einem Gehäuse, wobei das Gehäuse von einem vorderen Kopf (5), einem Zylinderblock (1), einem hinteren Kopf (3) und einem Deckelelement (38) gebildet ist, wobei das Gehäuse Folgendes aufweist:
    einen Abströmbereich, durch den aus einem Kompressionsraum abgeführtes Kältemittel aus dem Kompressor ausströmt,
    ein Rückschlagventil, das in dem Abströmbereich angeordnet ist, wobei der Abströmbereich gebildet ist mit
    einer Schalldämpferkammer (37),
    einem Rückschlagventilgehäuseabschnitt (44), der bezüglich der Schalldämpferkammer (37) stromabwärts gelegen ist, wo das Rückschlagventil (43) aufgenommen ist,
    einem Abströmdurchlass (45), der mit hochdruckseitigen Rohrleitungen eines Kältemittelkreislaufs verbunden und im Wesentlichen parallel zu dem Rückschlagventilgehäuseabschnitt (44) gebildet ist, und
    einem Verbindungsdurchlass (46), der eine Verbindung zwischen dem Rückschlagventilgehäuseabschnitt (44) auf einer Abströmseite des Rückschlagventils (43) und dem Abströmdurchlass (45) darstellt, wobei der Rückschlagventilgehäuseabschnitt (44), der Verbindungsdurchlass (46) und der Abströmdurchlass (45) in Reihe ausgehend von der Schalldämpferkammer (37) auf der stromabwärtigen Seite der Schalldämpferkammer (37) gebildet sind, dadurch gekennzeichnet, dass
    der Abströmbereich im Gehäuse gebildet ist.
  2. Kupplungsloser Kompressor mit variabler Verdrängung nach Anspruch 1, dadurch gekennzeichnet, dass ein Raum, der nur einem stromabwärtsseitigen Ende des Rückschlagventils (43) zugewandt ist, an dem Rückschlagventilgehäuseabschnitt (44) gebildet ist.
  3. Kupplungsloser Kompressor mit variabler Verdrängung nach Anspruch 1, bei dem ein Raum um das Rückschlagventil (43) an dem Rückschlagventilgehäuseabschnitt (44) gebildet ist.
  4. Kupplungsloser Kompressor mit variabler Verdrängung nach einem der Ansprüche 1 bis 3, der ferner Folgendes aufweist: ein Sicherheitsventil, das mit der Schalldämpferkammer (37) in Verbindung steht und das entsprechend der Höhe des Drucks in der Schalldämpferkammer (37) in Betrieb genommen werden kann.
  5. Kupplungsloser Kompressor mit variabler Verdrängung nach Anspruch 1 oder 3, der ferner Folgendes aufweist: ein Sicherheitsventil (49), das mit dem Abströmdurchlass (45) in Verbindung steht und das entsprechend der Höhe des Drucks auf der stromabwärtigen Seite des Rückschlagventils (43) in Betrieb genommen werden kann.
  6. Kupplungsloser Kompressor mit variabler Verdrängung nach Anspruch 5, dadurch gekennzeichnet, dass das Sicherheitsventil (49) an einer Leitung angeordnet ist, die sich von dem Verbindungsdurchlass (46) erstreckt.
  7. Kupplungsloser Kompressor mit variabler Verdrängung nach einem der Ansprüche 1 bis 6, wobei der kupplungslose Kompressor mit variabler Verdrängung ein kupplungsloser Taumelscheibenkompressor ist, mit: einer Welle (7), die durch einen Kurbelkasten (4) verläuft und drehbar an einem Gehäuse gelagert ist, einer Taumelscheibe (20), die sich synchron mit der Welle (7) dreht und bezüglich der Welle (7) kippbar angeordnet ist, einem Kolben (16), der an einem Umfangsrand der Taumelscheibe (20) gehalten ist und sich innerhalb einer an dem Gehäuse gebildeten Zylinderbohrung (15) in einer hin- und hergehenden Gleitbewegung befindet, wenn sich die Taumelscheibe (20) dreht, und einem Saugbereich und einem Abströmbereich, die wahlweise mit der Zylinderbohrung (15) in Verbindung stehen, wenn der Kolben (16) hin und her gleitet, wobei die Abströmverdrängung durch Verstellen des Winkels, in dem die Taumelscheibe (20) kippt, gesteuert ist.
EP07706626.4A 2006-01-30 2007-01-12 Kupplungsloser verdichter mit variabler verdrängung Not-in-force EP1983191B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006021233A JP5240535B2 (ja) 2006-01-30 2006-01-30 可変容量型クラッチレス圧縮機
PCT/JP2007/050279 WO2007086261A1 (ja) 2006-01-30 2007-01-12 可変容量型クラッチレス圧縮機

Publications (3)

Publication Number Publication Date
EP1983191A1 EP1983191A1 (de) 2008-10-22
EP1983191A4 EP1983191A4 (de) 2012-04-25
EP1983191B1 true EP1983191B1 (de) 2015-09-16

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Family Applications (1)

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EP07706626.4A Not-in-force EP1983191B1 (de) 2006-01-30 2007-01-12 Kupplungsloser verdichter mit variabler verdrängung

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EP (1) EP1983191B1 (de)
JP (1) JP5240535B2 (de)
WO (1) WO2007086261A1 (de)

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Publication number Priority date Publication date Assignee Title
CN101749225B (zh) * 2010-01-19 2012-05-23 西安交通大学 一种压缩机阀腔气流脉动衰减器
JP5697022B2 (ja) * 2010-12-14 2015-04-08 サンデン株式会社 可変容量圧縮機
JP6181429B2 (ja) 2013-05-29 2017-08-16 サンデンホールディングス株式会社 圧縮機

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KR100203975B1 (ko) * 1995-10-26 1999-06-15 이소가이 치세이 캠 플레이트식 가변용량 압축기
JP3587012B2 (ja) * 1996-03-12 2004-11-10 株式会社豊田自動織機 クラッチレス圧縮機
JP3582284B2 (ja) * 1997-03-13 2004-10-27 株式会社豊田自動織機 冷凍回路及び圧縮機
JPH11324919A (ja) * 1998-05-11 1999-11-26 Toyota Autom Loom Works Ltd 共振抑制方法および共振抑制装置
JP2000346241A (ja) * 1999-06-07 2000-12-15 Toyota Autom Loom Works Ltd 逆止弁
EP1365150B1 (de) * 2001-01-29 2016-08-24 Zexel Valeo Climate Control Corporation Verdrängungsverdichter ohne taumelscheibenkupplung
JP4734623B2 (ja) * 2003-09-24 2011-07-27 株式会社ヴァレオジャパン 可変容量型クラッチレス圧縮機

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Publication number Publication date
JP2007205165A (ja) 2007-08-16
WO2007086261A1 (ja) 2007-08-02
WO2007086261A8 (ja) 2007-09-20
EP1983191A1 (de) 2008-10-22
JP5240535B2 (ja) 2013-07-17
EP1983191A4 (de) 2012-04-25

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