KR101986287B1 - Device for compressing a gaseous fluid - Google Patents

Device for compressing a gaseous fluid Download PDF

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Publication number
KR101986287B1
KR101986287B1 KR1020180036288A KR20180036288A KR101986287B1 KR 101986287 B1 KR101986287 B1 KR 101986287B1 KR 1020180036288 A KR1020180036288 A KR 1020180036288A KR 20180036288 A KR20180036288 A KR 20180036288A KR 101986287 B1 KR101986287 B1 KR 101986287B1
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South Korea
Prior art keywords
wall
orbiter
base plate
openings
opening
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KR1020180036288A
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Korean (ko)
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KR20180131376A (en
Inventor
우베 포스첸리에더
토마스 클로튼
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한온시스템 주식회사
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/18—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber
    • F04C28/22—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • 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
    • F04C29/0042—Driving elements, brakes, couplings, transmissions specially adapted for pumps
    • F04C29/005—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
    • F04C29/0057—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions for eccentric movement
    • 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
    • F04C2240/00—Components
    • F04C2240/70—Use of multiplicity of similar components; Modular construction

Abstract

The present invention relates to an apparatus (1) for compressing a gaseous fluid. The device 1 comprises a housing 2 having a wall 12, a floating plate 3 extending from the side of the base plate 3a and having a spirally formed wall 3b, And an orbiter 4 extending from the front face of the base plate 4a and having a spiral wall 4b. In this case, the base plates 3a and 4a are arranged so that the wall 3b of the stator 3 and the wall 4b of the orbiter 4 are engaged with each other to form closed working areas 5 . The volume and the position of the work areas 5 are varied as a reaction to the motion of the orbiter 4. The device 1 also comprises a guide device 11 (not shown) having one or more openings 11a and one or more pins 11b for preventing rotation of the movable orbiter 4, Wherein the guide device is formed between the rear surface of the base plate 4a of the orbiter 4 and the wall 12. [ The at least one pin 11b is inserted into the at least one opening 11a depending on the position of the movable orbiter 4 relative to the wall 12 and the fixed stator 3. The central axes of the one or more openings 11a and the central axes of the one or more pins 11b are respectively connected to the movable orbiter 4 or the drive shaft 6 by a maximum pitch circle radius R ).

Description

TECHNICAL FIELD [0001] The present invention relates to a device for compressing a gaseous fluid,

The present invention relates to a device for compressing gaseous fluids, in particular refrigerant.

The apparatus comprises a housing having a wall, a base plate and an immovable / fixed stator extending from a side of the base plate and having a spirally formed wall, and a base plate extending from a front side of the base plate , And an obiter with a spirally formed wall.

The base plates are disposed facing each other such that walls of the stator and walls of the orbiter are engaged to form closed work areas. The volume and position of the working areas are varied as a reaction to the motion of the orbiter.

In addition, a guide device is provided to prevent rotation of the movable orbiter with respect to the floating stator, but to enable circular motion.

BACKGROUND OF THE INVENTION [0002] A compressor for mobile applications, particularly for automotive air conditioning systems, for transferring refrigerant through a refrigerant circulation system, also known as refrigerant compressors, known in the prior art, is a piston compressor with variable stroke volume independent of refrigerant Shaped or formed as a scroll compressor in many cases. At this time, the compressor is driven through a belt pulley or electrically driven.

Figures 1a and 1b each disclose a scroll compressor 1 ', known in the prior art, in cross-section, and in figure 1c, a plan view.

The conventional scroll compressor 1 'comprises a housing 2, a disc-shaped base plate 3a and a floating body 3b extending from the side of the base plate 3a and having a spirally formed wall 3b. A movable orbiter 4 having a stationary stator 3 and a disk-shaped base plate 4a and a wall 4b extending from the front surface of the base plate 4a and formed in a spiral shape.

The obturator 4 interacts with the stator 3, also referred to as a floating or stationary spiral portion 3 or a movable spiral portion 4. In this case, the base plates 3a and 4a are disposed so as to face each other so that the wall 3b of the stator 3 and the wall 4b of the obiter 4 are engaged with each other.

The movable spiral portion 4 is moved on the circular path by the eccentric drive. As such, when the spiral portion 4 moves, the walls 3a, 4b contact at a number of locations and form a number of successive, enclosed working areas 5 within the walls 3b, 4b , In which case the adjacent work areas 5 limit the volumes of different sizes.

The volume and position of the work areas 5 are varied in reaction to the motion of the orbiter 4. The volume of the work areas 5 becomes smaller toward the center of the spiral walls 3b and 4b, also called spiral walls.

The eccentric drive is formed from a drive shaft (6) and an intermediate member (8) that rotate about a rotary shaft (7). The drive shaft 6 is supported on the housing 2 through a first bearing 9.

The orbiter 4 is eccentrically connected with the drive shaft 6 through the intermediate member 8, that is, the axes of the orbiter 4 and the drive shaft 6 are arranged offset from each other. The orbiter (4) is supported on the intermediate member (8) through the second bearing (10).

The scroll compressor 1 'included in the prior art also comprises a guide device 11' which prevents the rotation of the movable spiral part 4 and prevents the rotation of the movable spiral part 4, Exercise makes possible.

The guide device 11 'generally comprises a plurality of circular openings 11'a, which are arranged adjacent to one another at regular intervals. In this case, the openings 11'a, which are preferably formed as blind holes, are formed on the rear surface of the base plate 4a of the movable spiral portion 4. [

Subsequently, the guide device 11 'is provided with pins 11'b, which are formed in a protruding form on the wall 12 of the housing 2, Is inserted into the opening 11'a formed in the opening 4a. The pins 11'b have a first end protruding from the wall 12 while a second end disposed within the wall 12 of the housing 2. [

WO 2015 060038 A1 discloses a scroll compressor with a guide device for preventing rotation of the movable spiral part but enabling circular motion. The guide device has openings formed in the base plate of the movable spiral portion, in which the pins are inserted. The pins are arranged to be inserted into a housing, in particular a hole formed in the housing.

JP 2009-281280 describes a scroll compressor having a cooling system of a rotational position adjusting mechanism of a movable spiral part. The component formed as a central plate of the housing has through-holes for the orientation guide pins of the movable spiral portion. Each of the guide pins is arranged to be inserted into one of the through holes.

1a and 1b, known scroll compressors 1 'are arranged on the wall 2, also referred to as the corresponding wall 12, which is arranged inside the housing 2 and which is fixed to this housing 2. [ 12). A back pressure region (13) is formed between the corresponding wall (12) and the movable spiral portion (4). Due to the widespread back pressure within the backpressure zone 13 the movable spiral part 4 is urged by force against the fixed spiral part 3 as if the corresponding wall 12 is fixed to the housing 2 Lt; / RTI >

In order to seal the back pressure region 13 and the suction region 14, a ring-shaped, in particular a circular ring, sealing member 15 'is arranged between the movable spiral portion 4 and the corresponding wall 12. The sealing member 15 'shown in the embodiment of the device 1' according to figures 1a to 1c has an inner diameter of, for example, about 80 mm.

The movable spiral portion 4 has a surface 16 oriented at one end to the corresponding wall 12. The sealing concept of the scroll compressor 1 'includes a sliding member 17 formed as a plate in addition to the sealing member 15', which is fixedly and floatingly connected to the housing 2, .

In this case, the plate-like stationary sliding member 17 disposed between the corresponding wall 12 and the spiral portion 4 is supported by the supporting surface 12 of the surface 16 of the movable spiral portion 4 having the sealing member 15 ' And to counteract the friction that occurs during the relative movement of the corresponding wall 12 and the spiral portion 4. [ In combination with the sealing member 15 ', the sliding member 17 seals the back pressure region 13 and the suction region 14 as pressure chambers to which two different pressures are supplied.

In addition, the sliding member 17 must contact the corresponding wall 12 of the housing 2 in a fluid-tight manner. Fluid-sealed connections are ensured by adhesion and lubricants, especially refrigerant oil mixtures. The sliding member 17 is formed from a material having excellent tribological properties and is corrosion-resistant and heat-resistant.

In conclusion, the movement of the movable spiral part 4 in relation to the stationary spiral part 3 in the trajectory of the trajectory of the movable spiral part 4 and of the movement of the movable spiral part 4 on the circular path, 4a provided on the rear side of the guide device 11 '.

In this case, the circular motion is caused by the intermediate member 8 engaging the radial center of the movable spiral portion 4, wherein the intermediate member is driven eccentrically by the crank pin disposed in the corresponding crank radius, And is fixed on the shaft 6.

The guide device 11 'prevents rotation of the movable spiral portion 4 which pivots about the central axis, in particular, about the rotational axis 7 of the drive shaft 6. The openings 11'a formed in the base plate 4a of the movable spiral portion 4 and the openings 11'a used as the guide member and circulating around the pins 11b ' And is also used to guide the movable spiral portion 4.

In this case the elements of the housing 2 arranged behind the movable spiral part 4 are arranged in the same angular division on the pitch circle radius R ' b are inserted into the openings 11'a of the movable spiral portion 4, which are formed in the form of a cylindrical pocket on the rear surface of the base plate 4a.

Circular ring-shaped sliding members are formed inside the cylindrical openings 11'a, and these sliding members reduce the surface wear of the openings 11'a and the pins 11'b. Circular ring-shaped sliding members used to support the orbital motion of the movable spiral portion 4 are in contact with the outer periphery of the openings 11'a (in particular according to FIGS. 1A and 1C).

Each of the pins 11'b slides along the inner side surface of each of the sliding members. Circular ring-shaped sliding members are also referred to as bearing rings.

The pitch circle radius R 'in which the pins 11'b of the guide device 11' in the wall 12 of the housing 2 are arranged is limited, The openings 11'a formed in the shape of a cylindrical pocket in the base plate 4a of the base plate 4a are widely used as sliding partners of the pins 11'b to accommodate widely closed sliding rings It must be formed in a closed form.

In this case, the bearing force F resulting from the torque acting on the movable spiral portion 4 about the central axis of the movable spiral portion 4 is again used as the pitch circle radius R 'as the lever arm L1. , But these pitch circle radii are limited in length.

The pitch circle radius R 'is, for example, 28.5 mm in the embodiment of the device 1' according to figures 1a-1c. Fig. 1d shows a diagram for the torque reception and force distribution together with the lever arm L1 of the guide device 11 'of the device 1' according to the prior art.

Japanese patent: JP 2009-281280

It is an object of the present invention to provide a device for compressing gaseous fluid using guide pins and openings of a guide device to prevent rotation of the movable spiral part to ensure maximum life of the device, , Especially to improve the scroll compressor.

In this case, the load, i.e. the force acting between the guide pins and the openings, must be minimized. At the same time, the device must be formed to withstand the high pressure of the fluid.

In addition, the apparatus should consist of as few individual components and components as possible. The device must be structurally simple to implement in order to minimize manufacturing and management costs.

This problem is solved by objects having the features of the independent patent claims. Improvements are described in the dependent patent claims.

This problem is solved by a device according to the invention for compressing gaseous fluids, in particular refrigerant. The apparatus includes a housing having a wall, a base plate, a floating stator extending from a side of the base plate and having a spirally formed wall, and a base plate and an orbiter extending from a front surface of the base plate and having a spirally formed wall Respectively. The base plates are disposed facing each other such that the walls of the stator and the walls of the orbiter are engaged with each other to form closed working areas. The volume and position of the working areas are varied as a reaction to the motion of the orbiter.

In addition, the device has a guide device for preventing rotation of the movable orbiter, but enabling circular motion, and this guide device has at least one opening and at least one pin. The guide device is formed between the rear surface of the base plate of the obiter and the housing wall. Wherein the one or more fins are inserted into the at least one opening according to the position of the movable orifice relative to the wall of the housing and the floating stator.

According to the idea of the invention, the central axis of the at least one opening of the guide device is arranged at a maximum pitch circle radius with respect to the axis of the movable orbiter or the drive shaft, and the central axis of the at least one pin of the guide device And is arranged with a maximum pitch circle radius with respect to the axis of the movable orbiter or the axis of rotation of the drive shaft. In this case, the axis of the movable orbiter and the axis of rotation of the drive shaft are aligned in parallel with each other.

In one improvement of the invention, one or more openings of the guide arrangement are formed in the rear face of the base plate of the orbiter and on the outer periphery of the base plate of the orbiter, and one or more pins are fixedly connected to the wall of the housing And protruding from the wall. Wherein the central axis of said at least one opening is arranged with a maximum pitch circle radius R with respect to the axis of the movable orbiter and the central axis of said at least one pin with a maximum pitch circle radius R with respect to the rotational axis of the drive shaft.

The one or more fins are preferably arranged in an opening formed in the wall, in particular in a blind hole, and being pressurized by the housing inside the opening.

According to an alternative first embodiment of the invention, the at least one opening of the guide device is formed as a circular segment as seen in a transverse section perpendicular to the axis of rotation and also to the axis of the movable orbiter.

Wherein the cross-section of said at least one opening preferably has an open pitch circle having an arc length forming an angle of at most 180 degrees.

The one or more fins thus abut the perimeter of the opening of the opening, which is inserted into the circular segment of the opening according to the position of the movable orifice relative to the wall of the housing and the movable stator, and which is formed as a circular arc in a transverse section perpendicular to the axis of rotation.

According to an alternative second embodiment of the invention, the at least one opening of the guide device is formed as a circular opening with a rotational axis and, in addition, a widely closed contour as viewed in cross-section perpendicular to the axis of the movable orbiter .

So that said at least one pin is always inserted into said circular opening and abuts against the cylindrical boundary wall of the opening, which is formed in a circle when viewed in cross section perpendicular to the axis of rotation depending on the position of the wall of the housing and the movable orbiter relative to the floating stator.

According to an improvement of the invention, the guide device has three or more openings and fins, in particular six openings and fins, respectively, and these openings and fins are each uniformly spaced by a pitch circle radius .

According to a preferred embodiment of the present invention, a circular ring-shaped sealing member for sealing the back pressure region and the suction region of the device is disposed between the movable orbiter and the wall of the housing.

In this case, the pitch circle radius of the guide device is preferably larger than the radius of the ring-shaped sealing member as a distance between the central axis of the opening of the movable orbiter or the rotational axis of the drive shaft and the central axis of the pin.

According to an alternative first embodiment of the present invention, the sealing member is arranged in such a manner as to protrude from the groove in the rear face of the movable orbiter, in such a manner as to protrude from the groove and in contact with the wall of the housing.

According to an alternative second embodiment of the present invention, the sealing member is arranged in a manner to protrude in such a manner as to protrude from such a groove and in contact with the rear surface of the movable orbiter, in the groove formed in the wall of the housing.

In conclusion, the device according to the invention for compressing gaseous fluids, in particular to provide a concept for guiding orbital motion as an improvement of the scroll compressor and as a minimum number of required components, Respectively.

- reduction of the load inside the guide part of the movable spiral part and the support part, that is,

The ring-shaped sliding members can be omitted inside the openings of the guide device in which less load is formed in the pocket shape, and as a result, the number of parts and individual components required for the track guide,

- a smaller required area in the radial direction of the semicircular openings of the guide means formed in the form of pockets is arranged on the rear face of the orbiter, making it possible to move the sealing member formed as a pressure chamber seal into the housing,

The sliding member can also be omitted, which reduces the number of necessary members and individual components,

- The maximum life of the device, as well as the device is designed to withstand the high pressure of the fluid to be compressed.

Further details, features and advantages of embodiments of the present invention will be apparent from the following description of embodiments with reference to the accompanying drawings. In the drawing:
Figs. 1A to 1C show a compression mechanism of a scroll compressor according to the prior art, in side elevation and in plan view, with a guide device for preventing rotation of the movable spiral part but enabling circular motion,
Figure 1d shows a schematic for torque reception and force distribution with lever arms of a guide device according to the prior art,
Figures 2a and 2b show a stator and an obturator forming a work area through interlocking helical walls and a scroll device with a guide device according to the invention for preventing rotation of the movable spiral part, The compression mechanism of the compressor is shown in a side sectional view and a plan view,
Fig. 2c shows a schematic for torque reception and force distribution with the lever arm of the guide device according to Figs. 2a and 2b.

2A and 2B show an apparatus 1 for compressing a gaseous fluid, in particular a scroll compressor, having a compression mechanism arranged in the housing 2 and composed of a stator 3 and an orbiter 4, And a plan view. The helical walls 3b, 4b, which are arranged on the base plates 3a, 4a respectively and engage with each other, form working spaces 5, this is particularly disclosed in FIG.

As the orbiter 4 is moved on the circular path through the eccentric drive, the helical wall 4b performs circular motion around the stationary helical wall 3b. When the helical walls 3b, 4b move relative to one another, these walls 3b, 4b contact a number of times and form a number of working areas 5 which become smaller inside the walls. As the two walls 3b and 4b, which are intertwined and helical, move in opposite directions, the working areas 5 are contracted and the fluid is compressed. The gaseous fluid to be compressed, in particular the refrigerant, is sucked and compressed inside the device 1 and then discharged through the outlet.

The drive shaft, which is not shown in the drawings, which drives the orbiter 4 is likewise held by a bearing, not shown in the figure, particularly supported by the housing 2 by means of a ball bearing. The drive shaft and the bearing rotate about the rotary shaft (7). In addition, the drive shaft is mechanically connected eccentrically with the orbiter 4, in particular via an intermediate member 8 as shown in figure 2b and an additional bearing not shown in the figure.

The wall 12 limits the backpressure zone 13 formed between the orbiter 4 and the housing 2 and also forms a separation wall between the backpressure zone 13 and the suction zone 14. In this case the backpressure zone 13 is formed in the rear face of the base plate 4a of the movable spiral part 4 in relation to the spiral wall 4b and the movable spiral part 4 is pressed against the fixed spiral part 3 Lt; / RTI > The back pressure region 13, also referred to as the back pressure chamber, is supplied with an intermediate pressure between the discharge pressure of the gaseous fluid and the suction pressure.

Between the corresponding wall 12 and the surface 16 of the movable spiral portion 4 oriented towards this corresponding wall 12 is a ring-shaped, especially an annular, A circular ring-shaped sealing member 15 is disposed. Therefore, in the groove formed in the surface 16, the sealing member 15 disposed in such a manner as to protrude from the groove abuts on the movable spiral portion 4 in the groove, and by the region protruding from the groove, (2). The sliding members known in the prior art (see Figs. 1A and 1B) can be omitted.

The sealing member 15 of the device 1 according to Figs. 2A and 2B has an inner diameter of, for example, about 63 mm, as compared with the device 1 'of the prior art according to Figs. 1A to 1C. Alternatively, the sealing member 15 'of the device 1' has a much larger diameter of about 80 mm.

It is possible to prevent the frictional heat which is generated when the helical walls 3b and 4b move with each other and when the helical wall 4b of the orbiter 4 moves towards the corresponding wall 12 and between the boundary surfaces of the working areas 5, In order to improve the sealing between the region 13 and the suction region 14, a lubricant, in particular oil, is added to the fluid.

The device 1 is also formed with a guide device 11 for preventing the rotation of the movable spiral part 4 in relation to the stationary spiral part 3, but for enabling circular motion.

The guide device 11 has a plurality of openings 11a and a pin 11b formed in the rear surface of the base plate 4a of the orbiter 4 in the direction of the back pressure region 13. [ These pins 11b are arranged at equal intervals from the rotary shaft 7 corresponding to the pitch circle radius R and uniformly distributed over the circumference. In the embodiment according to Figs. 2A and 2B, the guide device 11 has six openings 11a and a pin 11b, respectively.

The pitch circle radius R of the embodiment of the device 1 according to Figs. 2a and 2b is 42.5 mm, for example compared to the prior art device 1 'according to Figs. 1a-1c, The prior art device 1 'has a much smaller pitch circle radius R' of about 28.5 mm.

The pins 11b are inserted into the opening 11a depending on the location and position of the movable spiral portion 4 relative to the wall 12 or stationary spiral portion 3. In this case, at least one pin 11b is always inserted into one or more openings 11a. At the same time, the openings 11a are formed as circular segments, also referred to as circular sections, respectively, when viewed in cross section perpendicular to the axis of rotation 7.

In this case, the circular segment means the partial area of the circular area limited by the chord of a circle, in which case the arc is defined as a circle, a related subset of the circumference, The connection distance of the two points is named as the circle of the circle. At this time, the diameter of the circle extending through the weight center point is the longest string of the circle.

In particular, in order to minimize the required bearing force, the central axis of the openings 11a is arranged in such a way that the edges of these openings 11a form an open pitch circle with an arc length forming a maximum angle of 180 [ R) in the radial direction.

The circular segment-shaped openings 11a formed in the outer radius of the base plate 4a of the movable spiral portion 4 are preferably formed by a simple milling process or a turning process.

The pins 11b are arranged in such a manner that they project into the opening 11a by the first end respectively or according to the location and position of the movable spiral portion 4 relative to the wall 12 , And the second end is connected to the housing (2). The openings 11a formed as recesses in the base plate 4a of the movable spiral portion 4 and the pins 11b formed as the position member and as the guide member are provided for guiding the movable spiral portion 4. [

The pins 11b disposed on the corresponding wall 12 of the housing 2 and disposed on the horizontally oriented plane through the diameter of the movable spiral portion 4 are in engagement with the associated openings 11a , Whereas the pins 11b disposed under the horizontally oriented plane through the diameter of the movable spiral portion 4 are positioned outside the associated opening 11a.

The pins 11b are each arranged in the openings formed in the wall 12, in particular in the blind holes, and are pressed by the housing 2 in these openings. The pins 11b ensure an optimal guiding environment of the movable spiral portion 4 in a continuous positive arrangement and in a mutually parallel arrangement.

The distance between the openings 11a and the pins 11b of the guide device 11 with respect to the rotary shaft 7, that is, the pitch circle radius R, (15). Therefore, the radius of the ring-shaped sealing member 15 is smaller than the pitch circle radius R of the circular arrangement of the pin 11b or the opening 11a of the guide device.

In this case, the openings 11a are arranged on the outside or at the outermost edge of the base plate 4a of the movable spiral portion 4 and at a maximum spacing with respect to the rotational axis 7 or with a maximum pitch circle radius R, Is formed by the maximum lever arm of the torque acting on the arm (1).

As a result of which a ring-shaped sealing member 15 arranged on the rear side of the guide device 11 and likewise the movable spiral portion 4 or a ring-shaped sealing member 15 fixed to the corresponding wall of the housing as compared to the prior art device 1 ' The radial arrangement of the ring-shaped flat sliding surface disposed at the same position is diverted.

The sealing member is offset inwardly in the radial direction, in which case it is also possible to offset outwardly in the radial direction of the openings 11a. Therefore, the installation space for the slidable member of the sealing member is also extended.

In particular, a relatively small radial space occupied by openings in the form of circular segments makes it possible to place the sealing member in the housing. According to an alternative but not shown in the drawings, the ring-shaped sealing member is formed in such a manner as to be fixed to the corresponding wall of the housing.

Thus, in the grooves formed in the corresponding walls, the sealing members arranged in such a way as to protrude from these grooves can be moved in the grooves to the corresponding wall of the housing and to the movable spiral part directly by the area protruding from the groove, It touches the surface of the spiral part.

By placing the sealing member in the corresponding wall of the housing, the movable spiral portion can be integrally formed as a separate member and in addition thereto, without additional components such as a sealing member. However, if the abrasion resistance is not sufficient, the movable spiral portion is provided with a wear protection layer, so that the seal member contacts the movable spiral portion in the wear protection layer region.

According to an alternative but not shown embodiment of the present invention, the pitch circle radius R of the openings is selected as large as possible so that the openings form an enclosed contour within the outer diameter of the continuously moved spiral portion do.

In this case, the guide device has a plurality of circular openings and fins formed in the base plate of the orbiter in the direction of the back pressure region. These pins are each formed in such a manner that the first end protrudes into the opening, while the second end is connected to the housing. The openings are preferably formed in the base plate of the movable spiral part as blind holes, in particular as cylindrical pockets.

In this case, the openings are arranged at the outer edge of the base plate of the movable spiral part and at a maximum spacing or maximum pitch circle radius with respect to the axis of rotation so that the cylindrical pockets are wide closed and the cross-sections of the openings are not formed solely of circular segments.

In this case, likewise, the radius of the ring-shaped sealing member is also smaller than the pitch circle radius of the circular arrangement of the pins or openings of the guide device.

2c, a diagram for torque reception and force distribution is presented with the lever arms L1, L2 of the guide device 11 of the device 1 of Figures 2a and 2b.

In this case, the bearing force F obtained by the torque acting on the movable spiral portion 4 about the center axis of the movable spiral portion 4 is again transmitted to the pitch circle radius R and the wall 12, And the location and position of the movable spiral portion 4 relative to the movable spiral portion 4.

The maximum lever arm L1 in the apparatus 1 of Figures 2a and 2b with six openings 11a and track guide pins 11b uniformly distributed over the circumference is located at the center of the orbiter 4 Corresponds to the radial spacing between the axis passing therethrough and the central axis of the openings 11a disposed on the orbiter (4). The minimum lever arm L2 is calculated at L2 / L1 ratio = sin 60 占 = 0.866 占 L2 = 0.866 占 L1.

The minimum lever arm L2 of the device 1 also increases as the lever arm of the device 1 ', as the pitch circle radius R increases relative to the pitch circle radius R' of the device 1 ' The force acting on the lateral side of the pin 11b and the opening 11a of the device 1 when the torque acting on the center axis of the device 1 is the same is greater than the pitch circle radius R ' Much less.

Only the torque is observed in order to guide the movable spiral portion 4 on the circulation path because the radial forces are absorbed by the contact of the walls 3b and 4b of the spiral portions 3 and 4. Thus, the loads received from the side faces of the pins 11b and the openings 11a associated with these pins are reduced in accordance with the anti-rotation moment.

By separating the radial force support and the torque support against the movable spiral part 4 the value of the line load between the flank 11b of the fins 11b and the opening 11a is reduced by the radial force between the spiral parts 3, Is less than the value of the directional force. When the pitch circle radius (R) increases, the line load value continuously decreases.

The effective contact radius increases and the wear of the guide device 11 is reduced as the line load between the force F acting with it or the side flank of the openings 11a decreases with the fins 11b, The use of the corresponding abrasion resistant material of section 4 may eliminate bearing rings disposed within openings 11a. Thus, the movable spiral portion 4 is supported directly on the fins 11b and without intermediate members.

When the circular openings are arranged on the maximum pitch circle radius R forming openings 11a in the form of circular segments and openings 11a with interrupted side faces, the openings 11a are guided for guiding purposes, It can be combined with the pins 11b of the housing 11 to perform only a limited angular range. These angular ranges are only 30 [deg.] Relative to the angular range of 60 [deg.] When forming circular openings with widely closed side faces in the arrangement of six openings 11a and fins 11b.

The formation of open and circular segment shaped openings 11a compel the stepwise division of the support function into the adjacent openings 11a. However, due to the significantly longer lever arms L1, L2 when the openings 11a are formed in the outer diameter of the base plate 4a of the movable spiral part 4, The force for supporting the torque acting about the guide axis of the motor is minimized. In this case, the acting force (F) or linear contact load is inversely proportional to the pitch circle radius (R).

As the force F acting as a contact load between the pins 11b and the side elevation of the openings 11a causing torque support to limit the rotation of the movable spiral portion 4 decreases, It is also possible to omit the additional bearing rings or sliding rings applied in the openings of the device 11. [ Also, the number of openings and pins made up of pairs of guide devices disposed around a larger pitch circle can be enlarged.

The minimum number of the openings 11a and the pins 11b formed in pairs of the guide devices 11 is at least three, and the maximum number is limited to nine, for example, depending on the installation space used.

As the pitch circle radius R increases, the torsion between the pins 11b and the openings 11a decreases when the nominal clearance space inside the guide device 11 is the same.

1 ', 1: scroll compressor, device
2: Housing
3: stator, fixed spiral part
3a: Base plate of fixed spiral part (3)
3b: wall of stationary spiral part 3
4: Orbiter, movable spiral part
4a: the base plate of the movable spiral part (4)
4b: a wall of the movable spiral portion 4
5: Work area
6: Drive shaft
7: the rotation shaft of the drive shaft 6
8: intermediate member having additional weight
9: First bearing
10: Second bearing
11, 11 ': guide device
11a, 11'a: opening
11b, 11'b: pin
12: wall, corresponding wall
13: back pressure region, back pressure chamber
14: Suction area
15, 15 ': sealing member
16: the surface of the movable spiral portion 4
17: Sliding member
L1, L2: Lever arm
R, R ': pitch circle radius

Claims (10)

CLAIMS 1. A compression device (1) for compressing gaseous fluid, the compression device comprising:
A housing (2) having a wall (12);
An immovable stator (3) having a base plate (3a) and a wall (3b) extending from the side of the base plate (3a) and formed in a spiral shape;
An obiter (4) having a base plate (4a) and a wall (4b) extending from the front face of the base plate (4a) and formed in a spiral shape,
The base plates 3a and 4a are formed in such a manner that the wall 3b of the stator 3 and the wall 4b of the orbiter 4 are engaged with each other to form closed working areas 5. [ Wherein the volume and position of the work areas (5) are changed in reaction to the motion of the orbiter (4)
Further comprising a guide device (11) for preventing rotation of the orbiter (4) having at least one opening (11a) and at least one pin (11b) and for enabling circular motion,
The guide device 11 is formed between the rear face of the base plate 4a of the orbiter 4 and the wall 12 and the at least one pin 11b is connected to the wall 12 and the floating stator 3 Is inserted into the at least one opening (11a) in accordance with the position of the orbiter (4)
Wherein a center axis of the one or more openings 11a and a center axis of the at least one pin 11b are spaced apart from each other by a maximum pitch circle radius of the axes of the orbiter 4 or the rotational axis 7 of the drive shaft 6. [ circle radius R,
Characterized in that the cross-section of said at least one opening (11a) has an open pitch circle with an arc length forming an angle of at most 180 degrees.
The method according to claim 1,
The at least one opening 11a is formed in the rear surface of the base plate 4a of the orbiter 4 or the outer circumference of the base plate 4a,
Wherein the at least one pin 11b is fixedly connected to the wall 12 of the housing 2 or in a manner projecting from the wall 12,
Wherein the center axis of the at least one opening (11a) is arranged with a maximum pitch circle radius (R) with respect to the axis of the orbiter (4)
Characterized in that the center axis of the at least one pin (11b) is arranged at a maximum pitch circle radius (R) with respect to the rotational axis (7) of the drive shaft (6).
3. The method of claim 2,
Characterized in that said at least one opening (11a) is formed as a circular segment when viewed in transverse section perpendicular to said axis of rotation (7).
delete 3. The method of claim 2,
Characterized in that said at least one opening (11a) is formed as a circular opening with a widely closed contour in the transverse section perpendicular to said axis of rotation (7).
The method according to any one of claims 1 to 3,
Characterized in that the guide device (11) has three or more openings (11a) and fins (11b), each of which is uniformly distributed around the circumference with a pitch circle radius (R) Compression device (1).
The method according to any one of claims 1 to 3,
Characterized in that a circular ring-shaped sealing member (15) for sealing the back pressure region (13) and the suction region (14) is arranged between the orbiter (4) and the wall (12) ).
8. The method of claim 7,
Wherein the pitch circle radius (R) of the guide device (11) is greater than the radius of the circular ring-shaped sealing member (15).
8. The method of claim 7,
Characterized in that the sealing member (15) is arranged in such a way as to protrude from the inside of the groove formed in the rear face of the orbiter (4) or in contact with the wall (12).
8. The method of claim 7,
Characterized in that the sealing member (15) is disposed in such a way as to protrude from the inside of the groove formed in the wall (12) or in contact with the rear face of the orbiter (4).
KR1020180036288A 2017-05-30 2018-03-29 Device for compressing a gaseous fluid KR101986287B1 (en)

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Citations (1)

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Publication number Priority date Publication date Assignee Title
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JPH10103259A (en) * 1996-09-27 1998-04-21 Daikin Ind Ltd Scroll compressor
JP4514493B2 (en) 2004-04-02 2010-07-28 サンデン株式会社 Scroll type fluid machinery
JP5270960B2 (en) 2008-05-22 2013-08-21 サンデン株式会社 Scroll compressor
JP5326660B2 (en) 2009-02-27 2013-10-30 株式会社豊田自動織機 Scroll compressor
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JP2012036833A (en) 2010-08-06 2012-02-23 Daikin Industries Ltd Scroll type fluid machine

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