WO2008119319A2 - Klimakompressor - Google Patents
Klimakompressor Download PDFInfo
- Publication number
- WO2008119319A2 WO2008119319A2 PCT/DE2008/000414 DE2008000414W WO2008119319A2 WO 2008119319 A2 WO2008119319 A2 WO 2008119319A2 DE 2008000414 W DE2008000414 W DE 2008000414W WO 2008119319 A2 WO2008119319 A2 WO 2008119319A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- spring
- air compressor
- compressor according
- air conditioning
- effective
- Prior art date
Links
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
- F04B27/14—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
-
- 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
-
- 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
- F04B27/1054—Actuating elements
-
- 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
- F04B27/20—Control of pumps with rotary cylinder block
- F04B27/22—Control of pumps with rotary cylinder block by varying the relative positions of a swash plate and a cylinder block
-
- 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
- F04B2201/00—Pump parameters
- F04B2201/12—Parameters of driving or driven means
- F04B2201/1204—Position of a rotating inclined plate
- F04B2201/12041—Angular position
Definitions
- the invention relates to a hubvolumenver monotonen air conditioning compressor, in particular for motor vehicles, with an engine for reciprocating in cylinders piston, the pistons are driven via an adjusting disc, such as swash plate or swivel ring or swash plate with an adjustable swivel angle and wherein the position of the swivel angle is affected by other effective in the engine compressive forces, inertial forces and spring forces.
- an adjusting disc such as swash plate or swivel ring or swash plate with an adjustable swivel angle and wherein the position of the swivel angle is affected by other effective in the engine compressive forces, inertial forces and spring forces.
- a hubvolumenver ratheren air conditioning compressor especially for motor vehicles, with an engine for reciprocating in cylinders piston, the pistons are driven via an adjusting disc, such as swash plate or swivel ring or swash plate, with adjustable swivel angle and the position of the swivel angle
- the force acting on the pivot angle position of the adjusting spring forces are represented by a spring with a higher spring stiffness and a counter spring with a lower spring stiffness.
- the spring with the higher rigidity acts in the swivel angle-increasing direction and the counter-spring with the lower spring stiffness acts in the swivel-angle-reducing direction.
- This spring design has the advantage that, due to this combination of springs with different characteristics, a discontinuity occurs in the course of the force swivel angle. Characteristic is achieved. By suitable selection of a spring and a counter-spring with a significantly different, softer characteristic results in a non-continuous run of the spring force amounts above the stroke of the mechanism, which hampers the expression harmonic oscillations by suppressing the lower oscillation arc. This advantageously leads to the fact that the machine does not tend to harmonious oscillations of the pivot mechanism to its rest position in the off mode of the air conditioning, as well as in cold power requirements, ie when switching on the air conditioning, safely starts by means of a control valve signal.
- a preferred embodiment of the air conditioning compressor is characterized in that the stiffer spring has a limited stroke by means of a maximum stroke stop, while the weaker opposing spring is optionally effective over the entire Schwenkwinkelhub. Also preferred is an air-conditioning compressor in which the stiffer spring in the maximum stroke stop determines the starting position of the swivel angle of the adjusting disk when the internal combustion engine is switched off and the air conditioning system is switched off. This has the advantage that the necessary for a safe start of the air compressor pivot angle position can be specified geometrically by the stop exactly and that correspondingly at this point either the much harder spring or the much softer spring, depending on the adjustment of the pivot angle, can come into effect ,
- an air-conditioning compressor is preferred in which the stop of the stiffer spring is displaceably arranged from a maximum stroke to a minimum stroke. Furthermore, an air-conditioning compressor is preferred in which the displaceable stop is represented by a displaceable locking ring and a recess or a long groove on the drive shaft.
- the sliding stop has the advantage that the stiffer spring can only be compressed up to a certain minimum stroke and is thus protected from overloading by further compression.
- an air compressor is preferred in which the stiffer spring is effective by the stop only in a limited angular range of the adjusting.
- an air-conditioning compressor is preferred in which the softer counter-spring is effective over the entire angular range of the adjusting disk. Since the softer counter spring, which works against the stiffer spring, is virtually ineffective in operation because of their relatively weak design against the stiffer spring, the stiffer spring takes over the actual spring force control over the swivel angle in the minimum swivel angle range. The softer Genfeder can therefore be effective over the entire angular range, without affecting the force of the stiffer spring. But the softer counter spring can also be in principle from the effective range of the stiffer spring with its spring stroke at the end and no longer expand.
- an air-conditioning compressor is preferred in which the minimum pivoting angle of the adjusting disk is greater than, equal to or less than zero degrees. Also preferred is an air-conditioning compressor in which the starting position swivel angle of the adjusting disk is greater than the minimum swiveling angle.
- An air conditioning compressor according to the invention is characterized in that the stiffer spring is only effective in the range of high rotational speeds of the air conditioning compressor when the air conditioning system is switched on. When the air conditioning system is switched off, the stiffer spring is effective over the whole speed range.
- an air-conditioning compressor is preferred, in which the softer opposing spring is effective in all speed ranges of the air conditioning compressor.
- Figure 1 shows a swash plate which abuts directly on a soft and a hard spring.
- Figure 2 shows the swash plate of Figure 1, wherein the stiff spring has a displaceable Maximalhubanschlag.
- FIG. 3 shows a guide device of a swivel ring with a guide sleeve on the shaft and otherwise the spring arrangements of FIG. 1.
- FIG. 4 shows a guide device of a swivel ring with a guide sleeve as in FIG. 3, but with a displaceable stop of the stiff spring as in FIG. 2.
- FIG. 5 shows a guide sleeve with a rigid disc spring on the guide sleeve and a soft opposing spring within the guide sleeve.
- FIG. 6 shows the force curve over the swivel angle for the machine variants from FIGS. 1 to 4.
- FIG. 7 shows the force curve for the machine variant from FIG. 5.
- a swash plate 1 is shown, wherein the swash plate 1 is pivotally and slidably guided on the shaft with a guide sleeve 5.
- a stiff spring 9 shown here by two opposing disc springs, is positioned on the shaft 7 by a step 11 on the shaft 7 against a maximum stroke stop and on the other side by a locking ring 13.
- a coil spring 15, which is decidedly softer in its spring stiffness than the double plate spring 9, strikes with its one end against a stop 17 of the shaft 7 and with its other end against a stop 19 of the guide sleeve 5.
- a pressure in the compressor and in the air conditioning is built by the starting angle of the swash plate 1 of the air compressor, which leads to a further swinging of the swash plate 1 and a higher mass flow in the air conditioner, the Size of the pivot angle by a corresponding control valve, which regulates the pressure in the drive room, is specified.
- the position of the guide sleeve 5 of the swashplate 1 is thus predetermined by the influence of the rigid spring 9 remaining in abutment, by the pressure conditions in the air conditioning compressor, the specifications by the control valve and the force of the softer spring 15.
- the minimum swing angle of the air compressor as described above, set.
- the plate spring 9 of Figure 1 is replaced by a spring assembly 21, and has a displaceable stop for the guide sleeve 5 by means of a sliding retaining ring 23, which is guided in a long groove 25 of the shaft.
- the locking ring 23 can thus be moved at high speeds of the engine maximum up to a second stop 27 and ensures that the spring assembly 21 can not be compressed further and thus protected against overloads. All other components are, as described in Figure 1, unchanged in their function, so that reference can be made to the description in Figure 1.
- FIG. 5 shows a spring arrangement which differs functionally from the illustrations in FIGS. 1 to 4.
- the swivel ring 31 is arranged on a guide sleeve 35, which contains a plate spring 37, which is displaceable with the guide sleeve 35.
- the function of this spring combination is to the effect that at low engine speed and high mass flow, so large swivel angle of the swing ring 31 of the air compressor, the guide sleeve 35 by means of the stiff spring 37, the coil spring 15 compresses and thus allows large swivel angle.
- the pivot angle of the pivot ring 31 is reduced by the corresponding pressure specifications of the control valve for the engine, so that additionally by relaxing the spring 15, the guide sleeve with the stiffer spring 37 to the left moves and reduces the swivel angle in the compressor.
- the stiffer spring 37 stops against the securing ring 13
- a spring force increase takes place in the direction of minimum pivot angle due to deformation of the spring 37.
- the stiff spring 37 thus has no biasing force, since the soft spring 15 is ineffective against the stiff spring 37. Otherwise, the functions are comparable to the previously described functions.
- the starting angle ⁇ -stop is again shown at point 46 on the axis 42.
- the soft spring according to the characteristic 44 With its spring force is effective.
- the hard spring 37 which is not in the prestressed state, but relaxed within the guide sleeve 35 is carried along, deform according to the characteristic curve 52 and thus a steep spring force increase in the direction of small pivoting angle to the minimum stop ⁇ -min, which, for example, at maximum engine speed and switched-off air conditioning, so if no mass flow is needed prevails.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Air-Conditioning For Vehicles (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2010500065A JP5389010B2 (ja) | 2007-03-29 | 2008-03-07 | エアコンコンプレッサ |
EP08715557.8A EP2142801B1 (de) | 2007-03-29 | 2008-03-07 | Klimakompressor |
US12/450,490 US8353680B2 (en) | 2007-03-29 | 2008-03-07 | Air conditioning compressor |
DE112008000650T DE112008000650A5 (de) | 2007-03-29 | 2008-03-07 | Klimakompressor |
CN2008800053586A CN101631955B (zh) | 2007-03-29 | 2008-03-07 | 空调压缩机 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007015039 | 2007-03-29 | ||
DE102007015039.5 | 2007-03-29 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO2008119319A2 true WO2008119319A2 (de) | 2008-10-09 |
WO2008119319A3 WO2008119319A3 (de) | 2008-11-27 |
Family
ID=39745452
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2008/000414 WO2008119319A2 (de) | 2007-03-29 | 2008-03-07 | Klimakompressor |
Country Status (6)
Country | Link |
---|---|
US (1) | US8353680B2 (de) |
EP (1) | EP2142801B1 (de) |
JP (1) | JP5389010B2 (de) |
CN (1) | CN101631955B (de) |
DE (1) | DE112008000650A5 (de) |
WO (1) | WO2008119319A2 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10012218B2 (en) | 2012-04-25 | 2018-07-03 | Sanden Holdings Corporation | Variable displacement compressor and swash place linkage connection |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4543043A (en) * | 1982-08-02 | 1985-09-24 | Borg-Warner Corporation | Variable displacement compressor |
DE4211695A1 (de) * | 1991-04-08 | 1992-10-15 | Zexel Corp | Taumelscheibenverdichter |
EP0953765A2 (de) * | 1998-04-13 | 1999-11-03 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Verstellbarer Taumelscheibenkompressor mit Kontrollventil |
US20020178906A1 (en) * | 2001-06-04 | 2002-12-05 | Visteon Global Technologies, Inc. | Variability control of variable displacement compressors |
EP1281867A2 (de) * | 2001-08-02 | 2003-02-05 | Kabushiki Kaisha Toyota Jidoshokki | Vorrichtung zur Dämpfung des Geräusches eines Kolbenverdichters |
EP1701036A1 (de) * | 2005-03-11 | 2006-09-13 | Sanden Corporation | Schiebscheibenverdichter mit veränderlicher Verdrängung |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS62218670A (ja) * | 1986-03-19 | 1987-09-26 | Diesel Kiki Co Ltd | 可変容量型揺動板式圧縮機 |
JPH0633769B2 (ja) * | 1988-04-20 | 1994-05-02 | 本田技研工業株式会社 | 可変容量式圧縮機における始動時の容量設定装置 |
JP2626292B2 (ja) * | 1991-03-30 | 1997-07-02 | 株式会社豊田自動織機製作所 | 容量可変型斜板式圧縮機 |
JPH08326655A (ja) * | 1995-06-05 | 1996-12-10 | Calsonic Corp | 斜板式コンプレッサ |
JPH10176655A (ja) * | 1996-12-13 | 1998-06-30 | Zexel Corp | 可変容量型斜板式圧縮機 |
JP2001295757A (ja) * | 2000-04-11 | 2001-10-26 | Toyota Industries Corp | 可変容量圧縮機 |
JP2003065224A (ja) * | 2001-08-28 | 2003-03-05 | Toyota Industries Corp | 可変容量型ピストン式圧縮機 |
JP2005233054A (ja) * | 2004-02-19 | 2005-09-02 | Toyota Industries Corp | 圧縮機 |
JP2005351207A (ja) * | 2004-06-11 | 2005-12-22 | Tgk Co Ltd | 可変容量圧縮機用制御弁 |
JP4331667B2 (ja) * | 2004-10-22 | 2009-09-16 | 株式会社テージーケー | 可変容量圧縮機用制御弁 |
-
2008
- 2008-03-07 EP EP08715557.8A patent/EP2142801B1/de not_active Not-in-force
- 2008-03-07 CN CN2008800053586A patent/CN101631955B/zh not_active Expired - Fee Related
- 2008-03-07 JP JP2010500065A patent/JP5389010B2/ja not_active Expired - Fee Related
- 2008-03-07 US US12/450,490 patent/US8353680B2/en not_active Expired - Fee Related
- 2008-03-07 WO PCT/DE2008/000414 patent/WO2008119319A2/de active Application Filing
- 2008-03-07 DE DE112008000650T patent/DE112008000650A5/de not_active Withdrawn
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4543043A (en) * | 1982-08-02 | 1985-09-24 | Borg-Warner Corporation | Variable displacement compressor |
DE4211695A1 (de) * | 1991-04-08 | 1992-10-15 | Zexel Corp | Taumelscheibenverdichter |
EP0953765A2 (de) * | 1998-04-13 | 1999-11-03 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Verstellbarer Taumelscheibenkompressor mit Kontrollventil |
US20020178906A1 (en) * | 2001-06-04 | 2002-12-05 | Visteon Global Technologies, Inc. | Variability control of variable displacement compressors |
EP1281867A2 (de) * | 2001-08-02 | 2003-02-05 | Kabushiki Kaisha Toyota Jidoshokki | Vorrichtung zur Dämpfung des Geräusches eines Kolbenverdichters |
EP1701036A1 (de) * | 2005-03-11 | 2006-09-13 | Sanden Corporation | Schiebscheibenverdichter mit veränderlicher Verdrängung |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10012218B2 (en) | 2012-04-25 | 2018-07-03 | Sanden Holdings Corporation | Variable displacement compressor and swash place linkage connection |
DE112013002240B4 (de) * | 2012-04-25 | 2021-05-20 | Sanden Holdings Corporation | Verdichter mit variabler Verdrängung und autonom verkleinertem mininmalen Neigungswinkel bei vergrößerter Drehzahl |
Also Published As
Publication number | Publication date |
---|---|
EP2142801A2 (de) | 2010-01-13 |
JP5389010B2 (ja) | 2014-01-15 |
JP2010522838A (ja) | 2010-07-08 |
WO2008119319A3 (de) | 2008-11-27 |
DE112008000650A5 (de) | 2009-12-10 |
CN101631955B (zh) | 2012-04-25 |
US20100150744A1 (en) | 2010-06-17 |
EP2142801B1 (de) | 2013-11-06 |
CN101631955A (zh) | 2010-01-20 |
US8353680B2 (en) | 2013-01-15 |
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