CA2407403A1 - Compressor - Google Patents
Compressor Download PDFInfo
- Publication number
- CA2407403A1 CA2407403A1 CA002407403A CA2407403A CA2407403A1 CA 2407403 A1 CA2407403 A1 CA 2407403A1 CA 002407403 A CA002407403 A CA 002407403A CA 2407403 A CA2407403 A CA 2407403A CA 2407403 A1 CA2407403 A1 CA 2407403A1
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- CA
- Canada
- Prior art keywords
- compressor
- cylinder
- compression
- slant
- space
- 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.)
- Abandoned
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Classifications
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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
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
- F04C18/3568—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member with axially movable vanes
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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
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/008—Hermetic pumps
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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
- F04C2240/00—Components
- F04C2240/60—Shafts
- F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Rotary Pumps (AREA)
Abstract
A compressor including a cylinder assembly having a compression space through which suction passages and discharge passages are connected, a rotation driving unit inserted into the compression space of the cylinder assembly to transfer a rotation force, a slant compression slanted plate installed in the compression space to divide the compression space into at least two parts and rotating by being connected to the rotation driving unit, and vane units attached on both sides of the slant compression plate to classify the partitioned compression space into a suction space and a compression. With this construction, a vibration and a noise can be reduced and a stable driving force can be obtained even with a relatively small capacity electric motor. In addition, since fluid can be compressed and discharged simultaneously in both sides of the slant compression plate, an excellent compression performance can be accomplished in a simple structure.
Description
COMPRESSOR
TECHNICAL FIELD
The present invention relates to a compressor, and particularly, to a s compressor installed in such devices like a refrigerating cycle system and contracting and exhausting fluid.
BACKGROUND ART
Generally, compressors are apparatuses changing a mechanical so energy into a compression energy of compressible fluid, and these can be divided into rotary compressors, reciprocating compressors, and scroll compressors.
Operations of the rotary compressor, the reciprocating compressor, and the scroll compressor are will be described as follows.
15 As shown in Figure 1, in the rotary compressor, a motor device unit M
installed inside a casing 1, then accordingly a rotator 2 and a rotating shaft 3 are rotated. At that time, a rolling piston 5 installed on an eccentric unifi 3a of the rotating shaft 3 rotates along with an inner peripheral surFace of a cylinder 4, and compresses the fluid sucked into a compressing space V
TECHNICAL FIELD
The present invention relates to a compressor, and particularly, to a s compressor installed in such devices like a refrigerating cycle system and contracting and exhausting fluid.
BACKGROUND ART
Generally, compressors are apparatuses changing a mechanical so energy into a compression energy of compressible fluid, and these can be divided into rotary compressors, reciprocating compressors, and scroll compressors.
Operations of the rotary compressor, the reciprocating compressor, and the scroll compressor are will be described as follows.
15 As shown in Figure 1, in the rotary compressor, a motor device unit M
installed inside a casing 1, then accordingly a rotator 2 and a rotating shaft 3 are rotated. At that time, a rolling piston 5 installed on an eccentric unifi 3a of the rotating shaft 3 rotates along with an inner peripheral surFace of a cylinder 4, and compresses the fluid sucked into a compressing space V
2 o through an inlet 4a and discharges the compressed fluid through an exhausting passage 4b. And the processes are repeated.
In the reciprocating compressor, as shown in Figure 2, the motor device unit M installed inside the casing 11 is operated, and accordingly the rotator 12 and a crank shaft 13 are rotated. And at that time, a piston 14 coupled on the eccentric unit 13a of the crank shaft 13 undergoes a linear reciprocating movement inside the compression space V of the cylinder 15, and compresses the fluid sucked through a valve assembly 16, and at the same time, discharges the fluid through the valve assembly 16. In addition, the processes are repeated.
As shown in Figure 3, the scroll compressor is operated as follows.
That is, the motor device unit M installed inside the casing 21, and accordingly the rotator 22 and the rotating shaft 23 are rotated. At that time, a turning scroll 24 connected to the eccentric unit 23a of the rotating shaft 23 performs to a turning movement by meshed with a fixed scroll 25. Therefore, the fluid is sucked, compressed, and discharged continuously.
Compressors operated as above compression mechanisms will be described as follows in views of structure, function, and reliability.
The rotary compressor shown in Figure 1 comprises the rotating shaft 3 including the eccentric unit 3a, the rolling piston 5 press-fitted into the eccentric unit 3a, and a plurality of balance weights 6 and 6' coupled to the rotator 2 in order to maintain the rotating balance of the eccentric unit 3a, whereby the number of the components is increased and the structure is complex.
2 o The eccentric unit 3a of the rotating shaft and the rolling piston 5 inserted into the eccentric unit 3a are located inside the compression space V of the cylinder 4, and therefore the compression volume is small comparing to the size of the compression devices unit and the compression efficiency is lowered because one compression stroke is made when the rotating shaft is rotated once.
Also, a rotating torque is increased by the plurality of balance weights 6, whereby the power consumption is increased.
The eccentric unit 3a and the rolling piston 5 formed on the rotating shaft 3 are eccentrically rotated, and therefore vibration noise is generated during rotating.
In addition, the reciprocating compressor shown in Figure 2 comprises the crank shaft 13 having the eccentric unit 13a, the piston 14 coupled to the crank shaft 13, and a balance weight 13b for balancing the rotating balance Zo of the eccentric unit 13a, whereby the number of components is increased and the structure is complex.
And a sliding contact surface between the piston 14 and the cylinder is large, therefore the amount of oil consumption is increased.
The piston 14 undergoes a linear reciprocating movement inside the 15 cylinder compression space V, and therefore the fluid is compressed.
Therefore, the amount of compression discharge may be large when the crank shaft 13 is rotated once, however, one compression stroke is made when the crank shaft 13 is rotated once, whereby the compression efficiency is lowered.
2 o Also, the rotating torque is increased by the eccentric unit 13a of the crank shaft 13 and the balance weight 13b, whereby the power consumption is increased.
The eccentric unit 13a formed on the crank shaft 13 is eccentrically rotated, and thereby the vibration noise is generated. In addition, the valve assembly 16 is operated when the suction and discharge processes are made, whereby the noise is increased.
The scroll compressor shown in Figure 3 comprises a rotating shaft 23 including the eccentric unit 23a, a turning scroll 24 having wraps 24a and 25a of involute curve form and a fixed scroll 25, and a balance weight 26 for balancing the rotating balance of the eccentric unit 23a, whereby the number of components are large and structure is very complex. In addition, it is difficult to fabricate the turning scroll 24 and the fixed scroll 25.
A plurality of compression pockets formed by the wrap 24a of the Zo turning scroll 24 and the wrap 25a of the fixed scroll 25 compress the fluid continuously, and therefore the compression efficiency is high. However, the turning movement of the turning scroll 24 and the eccentric movement of the eccentric unit 23a of the rotating shaft 23 make big vibration noise.
As described above, the rotary compressor, the reciprocating i5 compressor, and the scroll compressor use the balance weights 6, 13b, and 26 because of the eccentric units 3a, 13a, and 23a of the shaft, and therefore the driving force is increased, the vibration and noise are generated, and the reliability is lowered.
In addition, in case of the rotary compressor and the reciprocating 2 o compressor, one compression stroke is made when the shaft is rotated once, and therefore it is not efficient. Especially, the rotary compressor has large dead volume, whereby the compression efficiency is lowered comparing to the size of the compression device unit.
In the reciprocating compressor, as shown in Figure 2, the motor device unit M installed inside the casing 11 is operated, and accordingly the rotator 12 and a crank shaft 13 are rotated. And at that time, a piston 14 coupled on the eccentric unit 13a of the crank shaft 13 undergoes a linear reciprocating movement inside the compression space V of the cylinder 15, and compresses the fluid sucked through a valve assembly 16, and at the same time, discharges the fluid through the valve assembly 16. In addition, the processes are repeated.
As shown in Figure 3, the scroll compressor is operated as follows.
That is, the motor device unit M installed inside the casing 21, and accordingly the rotator 22 and the rotating shaft 23 are rotated. At that time, a turning scroll 24 connected to the eccentric unit 23a of the rotating shaft 23 performs to a turning movement by meshed with a fixed scroll 25. Therefore, the fluid is sucked, compressed, and discharged continuously.
Compressors operated as above compression mechanisms will be described as follows in views of structure, function, and reliability.
The rotary compressor shown in Figure 1 comprises the rotating shaft 3 including the eccentric unit 3a, the rolling piston 5 press-fitted into the eccentric unit 3a, and a plurality of balance weights 6 and 6' coupled to the rotator 2 in order to maintain the rotating balance of the eccentric unit 3a, whereby the number of the components is increased and the structure is complex.
2 o The eccentric unit 3a of the rotating shaft and the rolling piston 5 inserted into the eccentric unit 3a are located inside the compression space V of the cylinder 4, and therefore the compression volume is small comparing to the size of the compression devices unit and the compression efficiency is lowered because one compression stroke is made when the rotating shaft is rotated once.
Also, a rotating torque is increased by the plurality of balance weights 6, whereby the power consumption is increased.
The eccentric unit 3a and the rolling piston 5 formed on the rotating shaft 3 are eccentrically rotated, and therefore vibration noise is generated during rotating.
In addition, the reciprocating compressor shown in Figure 2 comprises the crank shaft 13 having the eccentric unit 13a, the piston 14 coupled to the crank shaft 13, and a balance weight 13b for balancing the rotating balance Zo of the eccentric unit 13a, whereby the number of components is increased and the structure is complex.
And a sliding contact surface between the piston 14 and the cylinder is large, therefore the amount of oil consumption is increased.
The piston 14 undergoes a linear reciprocating movement inside the 15 cylinder compression space V, and therefore the fluid is compressed.
Therefore, the amount of compression discharge may be large when the crank shaft 13 is rotated once, however, one compression stroke is made when the crank shaft 13 is rotated once, whereby the compression efficiency is lowered.
2 o Also, the rotating torque is increased by the eccentric unit 13a of the crank shaft 13 and the balance weight 13b, whereby the power consumption is increased.
The eccentric unit 13a formed on the crank shaft 13 is eccentrically rotated, and thereby the vibration noise is generated. In addition, the valve assembly 16 is operated when the suction and discharge processes are made, whereby the noise is increased.
The scroll compressor shown in Figure 3 comprises a rotating shaft 23 including the eccentric unit 23a, a turning scroll 24 having wraps 24a and 25a of involute curve form and a fixed scroll 25, and a balance weight 26 for balancing the rotating balance of the eccentric unit 23a, whereby the number of components are large and structure is very complex. In addition, it is difficult to fabricate the turning scroll 24 and the fixed scroll 25.
A plurality of compression pockets formed by the wrap 24a of the Zo turning scroll 24 and the wrap 25a of the fixed scroll 25 compress the fluid continuously, and therefore the compression efficiency is high. However, the turning movement of the turning scroll 24 and the eccentric movement of the eccentric unit 23a of the rotating shaft 23 make big vibration noise.
As described above, the rotary compressor, the reciprocating i5 compressor, and the scroll compressor use the balance weights 6, 13b, and 26 because of the eccentric units 3a, 13a, and 23a of the shaft, and therefore the driving force is increased, the vibration and noise are generated, and the reliability is lowered.
In addition, in case of the rotary compressor and the reciprocating 2 o compressor, one compression stroke is made when the shaft is rotated once, and therefore it is not efficient. Especially, the rotary compressor has large dead volume, whereby the compression efficiency is lowered comparing to the size of the compression device unit.
DETAILED DESCRIPTION OF THE INVENTION
Therefore, an object of the present invention is to provide a compressor including a slant compression plate having an upper dead center and a lower dead center inside a compression space, whereby entire structure can be simple, vibration and noise are lowered, and compression efficiency per unit volume is increased.
In order to achieve the above objects, there is provided a compressor comprising: a cylinder assembly having a compression space therein, and a suction flowing passage and a discharge flowing passage are connected to to the compression space; a rotation driving means inserted inside the compression space of the cylinder assembly for transmitting the rotational force; a slant compression plate located inside the compression space of the cylinder assembly for dividing the compression space into two or more spaces, and at the same time, compressing and discharging fluid in the z5 respective spaces through the discharge flowing passage while rotating by being connected to the rotation driving means; and a vane means adhered to both surfaces of the slant compression plate by being inserted inside the compression space of the cylinder assembly so as to perform reciprocating movement, and dividing the respective spaces partitioned by the slant 2 o compression plate into a suction space and a compression space by being located between the suction flowing passage and the discharge flowing passage.
The cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by being coupled to the upper and lower parts of the cylinder and at the same time, supporting the rotation driving means.
A damping recess of a certain depth is formed in the cylinder assembly so as to suck a pressure pulsation generated during fluid compression process inside the compression space.
The suction flowing passage and the discharge flowing passage are formed as two pairs so as to have phase difference of 180°.
A discharge valve is formed on the discharge flowing passage of the cylinder assembly for opening/closing the discharge of the compressed fluid.
to Two suction flowing passages are formed in the cylinder so as to have phase difference of 180°, one of those two is formed on an upper part of the cylinder and the other is formed on a lower part of the cylinder.
A flowing resistance reducing unit which is an emitted part is formed on an entrance unit located on the compression space side of the cylinder z5 assembly so that the flowing resistance generated when the compressed fluid is discharged can be reduced.
A plurality of vane slots are formed on the bearing plates so that the vane means can be inserted and undergoes the reciprocating movement.
A coupling protrusion unit of round shape, which is protruded to inside 20 of the compression space as a certain height and has a outer diameter corresponding to an inner diameter of the cylinder, is formed on the bearing plates.
The slant compression plate is formed to have a plane surface having a plane surface formed as a ring round disk form, and a side surface formed as a sine wave having a upper dead center and a lower dead center adhered to an upper side surface and to a lower side surface of the compression space.
The upper dead center and the lower dead center of the slant compression plate are formed to have a phase difference of 180°, and an angle of a certain horizontal line from the outer circumferential surface to the inner circumferential surface and an outer surface in vertical direction of the rotation driving means is formed to make a right-angle.
The upper dead center and the lower dead center of the slant Zo compression plate may be formed as a curved surface so as to line contact to the upper surface and to the lower surface of the compression space, or may be formed as a plane surface so as fio surface contact to the upper and lower surfaces of the compression space.
The slant compression plate includes a labyrinth seal having afi least s5 one recess band on the outer circumferential surface which is slide contacted to the cylinder assembly so as to prevent a leakage of the fluid from high-pressure side to the low-pressure side by the pressure difference between the respective compression spaces.
The vane means comprises a vane of square shape adhered to the 2 o slant compression plate inside the compression space of the cylinder assembly, and an elastic supporting means supported by the cylinder assembly and providing an elastic force so that the vane is adhered to the slant compression plate.
The vane is disposed on the cylinder assembly to have a phase difference of 180°, and to be adhered to the upper and lower surfaces of the slant compression plate.
The elastic supporting means comprises a spring retainer supported by the cylinder assembly, and a spring supported by the spring retainer for s providing an elastic force to the vane.
A side surface of the vane is formed to be a concave surface so as to surface contact to the outer circumferential surface of the rotating shaft, and the other side surface of the vane is formed to be a convex surface so as to surface contact to the inner circumferential surface of the cylinder assembly.
so The vane comprises a contact curved surface unit of round shape formed on a porfiion to which the slant compression plate is contacted, and the contact curved surface is formed to be enlarged its radius of curvature from the rotational center of the slant compression plate to the outer circumferential surface.
15 According to another embodiment of the present invention, the cylinder assembly has two compression spaces centering around the slant compression plate. In addition, a first suction passage and .a first discharge passage are connected to the first compression space, and a second suction passage and a second discharge passage are connected to the second z o compression space.
The first discharge passage is connected to the second suction passage, whereby the fluid compressed in the first compression space is re-compressed in the second compression space.
According to still another embodiment of the present invention, the s vane means are respectively disposed on same vertical surFace of the cylinder assembly so as to adhere to the upper surface and the lower surface of the slant compression plate.
Two discharge passages are formed in side direction of the cylinder assembly, and some parts of the respective discharge passages are overlapped with the vane means.
The suction passage is formed on side wall of the cylinder assembly so that the fluid is sucked into the both compression spaces in turns accordinc to the rotation of the slant compression plate.
1o A spring penetrating hole is formed on the cylinder assembly so that the elastic supporting means can be passed, and the elastic supporting means is connected to the vanes located on the upper and lower sides of the slant compression plate through the spring penetrating hole, whereby the elastic force can be provided.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a cross-sectional view showing a general rotary compressor;
Figure 2 is a cross-sectional view showing a general reciprocating 2 o compressor;
Figure 3 is a cross-sectional view showing a general scroll compressor;
Figure 4 is a longitudinal cross-sectional view showing a compressor according to a first embodiment of the present invention;
Figure 5 is a transverse cross-sectional view showing the compressor according to the first embodiment of the present invention;
Figures 6A, 6B, and 6C are cross-sectional views of line A-A', fine B-B', and line C-C' in Figure 5;
Figure 7 is a cut perspective view showing principal parts of the compressor of the first embodiment according to the present invention;
Figures 8 through 10 are longitudinal cross-sectional view and plane cross-sectional views of principal parts showing operation states of the compressor of the first embodiment according to the present invention;
1o Figure 11 is a longitudinal cross-sectional view showing a compressor of a second embodiment according to the present invention;
Figure 12 is a cut perspective view of principal parts showing the compressor of the second embodiment according to the present invention;
Figures 13A and 13B are longitudinal cross-sectional views showing 25 operation state of the compressor of the second embodiment according to the present invention;
Figure 14 is a view showing status of fluid flowing in the compressor of the second embodiment according to the present invention;
Figure 15 is a longitudinal cross-sectional view showing a compressor 20 of a third embodiment according to the present invention;
Figures 16A, 16B are a transverse cross-sectional view showing the compressor of the third embodiment of the present invention, and a cross-sectional view of line D-D';
Figure 17 is a cut perspective view of principal parts showing the compressor of the third embodiment according to the present invention;
Figures 18A and 18B are cross-sectional views of principal parts showing an another embodiment of a damping recess in the compressor of the third embodiment according to the present invention;
Figure 19 is a transverse cross-sectional view and an enlarged view of principal parts showing a compressor of a fourth embodiment according to the present invention;
Figure 20 is a longitudinal cross-sectional view and an enlarged view showing the compressor of fourth embodiment according to the present invention;
Figures 21 A, 21 B, and 21 C are detailed cross-sectional views of principal parts showing modified embodiments of the damping recess in the compressor of the fourth embodiment according to the present invention;
Figure 22 is a longitudinal cross-sectional view of principal parts s5 showing a compressor of a fifth embodiment according to the present invention;
Figure 23 is a cut perspective view of principal parts showing the compressor of the fifth embodiment according to the present invention;
Figure 24 is a transverse cross-sectional view showing the compressor 2 0 of the fifth embodiment according to the present invention;
Figure 25 is a cut perspective view of principal parts showing a compressor of a sixth embodiment according to the present invention;
Figure 26 is a longitudinal cross-sectional view and detailed view showing the compressor of the sixth embodiment according to the present invention;
Figures 27A and 27B are detailed cross-sectional views of principal parts showing modified embodiments of a flowing resistance reducing unit in the compressor of the sixth embodiment according to the present invention;
Figure 28 is a longitudinal cross-sectional view of principal parts showing a compressor of a seventh embodiment according to the present invention;
Figure 29 is a detailed cross-sectional view of line E-E' in Figure 28;
Figure 30 is a transverse cross-sectional view showing the compressor of the seventh embodiment according to the present invention;
Figure 31 is a cut perspective view of principal parts showing the compressor of the seventh embodiment according to the present invention;
Figure 32 is a cuff perspective view of principal parts showing a compressor of an eighth embodiment according to the present invention;
Figure 33 is a longitudinal cross-sectional view of principal parts showing the compressor of the eighth embodiment according to the present invention;
Figure 34 is a detailed cross-sectional view of line F-F' in Figure 33;
Figure 35 is a longitudinal cross-sectional view of principal parts 2 o showing a compressor of a ninth embodiment according to the present invention;
Figure 36 is a cut perspective view of principal parts showing the compressor of the ninth embodiment according to the present invention;
Figure 37 is a detailed view of principal parts showing the compressor of ninth embodiment according to the present invention;
Figure 38 is a longitudinal cross-sectional view showing a compressor of a tenth embodiment according to the present invention;
Figure 39 is a transverse cross-sectional view showing the compressor of the tenth embodiment according to the present invention;
Figure 40 is a cut perspective view showing the compressor of the tenth embodiment according to the present invention;
Figure 41 is a transverse cross-sectional view of principal parts for describing the compression processes of the compressor of the tenth to embodiment according to the present invention;
Figures 42A, 42B, 42C, and 42D are longitudinal cross-sectional views showing the compression processes of the compressor of the tenth embodiment according to the present invention;
Figure 43 is a longitudinal cross-sectional view showing a compressor 15 of an eleventh embodiment according to the present invention;
Figures 44A and 44B are detailed cross-sectional views of principal parts showing operation state of a vane of the eleventh embodiment according to the present invention;
Figure 45 is a longitudinal cross-sectional view showing a compressor 20 of a twelfth embodiment according to the present invention;
Figure 46 is a cut perspective view showing the compressor of twelfth embodiment according to the present invention;
Figures 47A, 47B, and 47C are a front view, a side view, and an enlarged perspective view of principal parts showing a structure of the vane in the compressor of twelfth embodiment according to the present invention;
Figures 48A and 48B are plane views showing operation state of the compressor of the twelfth embodiment according to the present invention;
Figure 49 is a plane view showing contact status of the vane in accordance with a rotation of the slant compression plate in the compressor of twelfth embodiment according to the present invention;
Figure 50 is a detailed view showing the contact status of the compression sieve unit and the vane in the compressor of the twelfth embodiment according to the present invention;
1 o Figure 51 is a cut perspective view showing a compressor of thirteenth embodiment according to the present invention;
Figure 52 is a detailed view showing a status of rotating the compressor as 180°;
Figure 53 is a plane view showing principal parts of the compressor 15 of the thirteenth embodiment according to the present invention; and Figure 54 is a perspective view showing a modified embodiment a shaft contact surface unit of the vane in the compressor of the thirteenth embodiment according to the present invention.
2 o MODE FOR CARRYING OUT THE PREFERRED EMBODIMENTS
The present invention will now be described with reference to accompanying drawings.
A compressor of a first embodiment according to the present invention will be described with reference to Figures 4 through 12.
Figure 4 is a longitudinal cross-sectional view showing the compressor of the first embodiment according to the present invention, Figure 5 is a transverse cross-sectional view showing the compressor of the first embodiment according to the present invention, Figure 6 is a cross-sectional view of principal parts of lines A-A', B-B', and C-C', and Figure 7 is a cut perspective view showing the compressor of the first embodiment according to the present invention.
The compressor of the first embodiment according to the present invention comprises a motor device unit M for generating a rotation force so inside a casing C, and a compression device unit P for compressing and discharging fluid.
The casing C is formed to have a certain inner volume so as to be sealed, and has at least one or more suction pipe 42 for sucking the fluid formed on one side of the casing and a discharge pipe 43 for discharging the fluid on the other side.
The motor device unit M comprises a stator 44 fixedly coupled to the casing C, and a rotator 45 coupled inside the stator 44 so as to be rotational.
The compression device unit P comprises a cylinder assembly 50 having a compression space V therein and a plurality of suction passages 53 2 o and discharge passages 54 communicating with the compression space V
respectively; a rotating shaft 61 coupled to a rotator 45 of the motor device unit M and penetrating a center portion of the cylinder assembly 50; a slant compression plate 70 coupled to the rotating shaft 61 inside the cylinder assembly 40 and dividing the compression space V of the cylinder assembly 50 into a first space V1, and a second space V2; a first vane 80 and a second vane 80' penetratingly inserted into the cylinder assembly 50, and elastically supported so as to confiact to the both side surfaces of the slant compression plate 70, whereby the vanes undergo a reciprocating movement according to the rotation of the slant compression plate 70 and dividing the compression spaces V1 and V2 as a suction space and a compression space so as to be changeable with each other; and a discharge valve 90 opening/closing the discharge passage 54 of the cylinder assembly and discharging the compressed fluid in the first and the second compression spaces V1 and V2.
1 o Components of the compression device unit P will be described in more detail as follows.
The cylinder assembly 50 comprises a cylinder 55 fixedly installed inside a casing C which has a suction pipe 42 and a discharge pipe 43, and a first bearing plate 56 and a second bearing plate 57 fixed on an upper and a lower sides of the cylinder 55 and forming the compression space V with the cylinder 55.
Herein, the cylinder 55 includes a compression space V therein, and suction passages 53 and 53' communicating with the compression space V
respectively are formed to have a phase difference of 180°.
2 o The suction passages 53 and 53' are formed to have sizes which are able to be opened/closes by the area of side surface thickness of the slant compression plate 70. The suction passage 53 of the first space is formed on upper end part of the cylinder 55, and the suction passage 53' of the second space is formed on lower end part of the cylinder 55.
Shaft holes 56b and 57b, through which the rotating shaft 60 is inserted, are formed on center parts of the first and second bearing plates 56 and 57. Vane slots 56a and 57a having a phase difference of 180° in vertical direction are formed on a side surfaces of the shaft holes 56b and 57b, and the suction passages 53 and 53' and the discharge passages 54 and 54' are disposed on both sides of the vane slots 56a and 57a.
In addition, a first discharge muffler 58 having a large are unit and a small area unit is installed on an upper part of the first bearing plate 56 in order to reduce discharging noise of the fluid discharged from the discharge so passage 54, and a second discharge muffler 59 having a large area unit and a small area unit is installed on a lower part of the second bearing plate 57 in order to reduce discharging noise of the fluid discharged from the discharge passage 54'.
As another embodiment of the cylinder assembly 50, the cylinder 55 15 and the first bearing plate 56 may be formed as a single body, and the second bearing plate 57 may cover the cylinder 55.
Also, as another embodiments of the cylinder assembly 50, the cylinder 55 and the second bearing plate 57 may be formed as a single body, and the first bearing plate 56 may cover the cylinder 55.
2 o In addition, the rotating shaft 60 is press-fitted into the rotator 45, and is penetratingly inserted into the cylinder assembly 50. That is, the rotating shaft 60 is penetratingly inserted into the shaft holes 56b and 57b of the first and second bearing plates 56 and 57, and supported by the first and second bearing plates 56 and 57 so as to rotate relatively.
And, the slant compression plate 70 is formed as ring round disc from plane view, and is formed as a sine wave having an upper dead center R1 and a lower dead center R2 from side view.
That is, on the slant compression plate 70, the upper dead center R1 and the lower dead center R2 are disposed with a phase difference of 180°
therebetween, and is formed as a sine wave when spreading out. And an outer circumferential surface of the slant compression plate 70 is formed as a round when projected from plane view so as to sliding contact to the inner circumferential surface of the cylinder 55.
so In addition, the upper dead center R1 is always slidingly contacted to a bottom surface of the first bearing plate 56, however the lower dead center R2 is disposed to slidingly contact to an upper surface of the second bearing plate 57.
Also, it is desirable that an angle made by a certain horizontal line connected from outer circumferential surface to the inner circumferential surface and by an outer surface of the hub unit 72 in vertical direction is right-angle on the slant compression plate 70.
It is desirable that the thickness of a part making the upper dead center R1 and the lower dead center R2 is formed so as to block the suction 2 o passages 53 and 53' of the cylinder 55 in the slant compression plate 70.
The rotating shaft 60 and the slant compression plate 70 may be formed such that the rotating shaft 60, the hub unit 72, and the slant compression plate 70 are formed as a single body, or these are molded separately and assembled.
Also, the rotating shaft 60 and the hub unit 72, or the hub unit 72 and the slant compression plate 70 may be formed as a single body, and then these may be coupled to another component.
In addition, the vanes 80 and 80' are formed as a square plate so as to have a certain thickness and area, and are inserted into the vane slots 56a and 57a formed on the first and the second bearing plates 56 and 57.
As shown in Figure 7, the vanes 80 and 80' are constructed so as to change the first space V1 and the second space V2 to suction spaces V1 s and V2s, and compression spaces V1 p and V2p respectively, when the slant 1 o compression plate 70 is rotated as contacted to the inner circumferential surface of the cylinder compression space V in the state that the vanes 80 and 80' are contacted to the hub unit 72, to the slant compression plate 70 which are located inside the cylinder compression space V, and to the inner circumferential surface of the cylinder compression space V.
In addition, the vanes 80 and 80' are elastically supported by the elastic supporting means 81 and 81', and the elastic supporting means 81 and 81' are supported by the first and the second bearing plates 56 and 57, respectively.
And, as shown in Figure 6A, the discharge valves 90 and 90' are 2 o installed on the first and the second bearing plates 56 and 57 respectively so as to open/close the discharge passages 54 and 54' through which the fluid compressed in the compression spaces V1 p and V2p of the first and the second spaces V1 and V2 is discharged.
On the other hand, on the bottom surface of the casing C, oil for lubricating and cooling functions is filled on a part where the compression device unit P and the motor device unit M are slidingly contacted. And an oil pump(not shown) for pumping the oil and as oil passage 61 are formed inside the rotating shaft 60.
Operation and effect of the first embodiment according to the present invention will be described as follows.
When an electric current is supplied to the motor device unit M, the rotator 45 and the rotating shaft 60 are rotated. At that time, the first space V1 and the second space V2 of the cylinder 55 are changed into the suction z o spaces V1 s and V2s and compression spaces V1 p and V2p respectively according to the rotation of the slant compression plate 70, and the fluid is sucked into the respective suction passages 53 and 53' of the first and the second spaces V1 and V2 and compressed, and then discharged through the respective discharge passages 54 and 54'.
s5 The processes of suction, compression, and discharging of the fluid according to the rotation of the slant compression plate 70 will be described in more detail with reference to Figures 8 through 10.
Figures 8 through 10 are longitudinal and plane cross-sectional views showing operation states of the compressor in the first embodiment according 2 o to the present invention.
The slant compression plate 70 divides the compression space V of the cylinder 55 into the first space V1 and the second space V2, and the upper dead center R1 and the lower dead center R2 are line contacted to the upper and lower surfaces of the compression space V.
In that state, as shown in Figure 8; when the upper dead center R1 and the lower dead center R2 of the slant compression plate 70 are located between the discharge passages 54 and 54' and the vanes 80 and 80' of the first and the second spaces V1 and V2 respectively, the fluid respectively compressed in the first and the second spaces 54 and 54' are discharged through the discharge passages 54 and 54'.
After that, as shown in Figure 9, when the slant compression plate 70 is rotated to counter-clockwise direction, and the upper and lower dead centers R1 and R2 of the slant compression plate 70 are located between the z o vanes 80 and 80' and the suction passages 53 and 53', then the suction of fluid into the first and the second space V1 and V2 is completed.
In addition, as shown in Figure 10, when the slant compression plate 70 is rotated to counter-clockwise direction, then the upper and lower dead centers R1 and R2 of the slant compression plate 70 are changed into the 15 suction spaces V1 s and V2s and the compression spaces V1 p and V2p in the first and second spaces V1 and V2 by the vane 80 from the position behind the suction passages 53 and 53' to the position before the discharge passages 54 and 54', the fluid in the compression spaces V1 p and V2p is compressed and discharged through the discharge passages 54 and 54', and 2 o at the same time, the fluid is sucked into the suction spaces V1 s and V2s through the suction passages 53 and 53' because of the volume change of the suction spaces V1 s and V2s.
That is, the suction spaces V1 s and V2s suck the fluid as the volume is enlarged, and the compression spaces V1 p and V2p compress the fluid as the volume therein is reduced. Through the processes above, the fluid is sucked, compressed, and discharged in the first and second spaces V1 and V2 at the same time according to the rotation of the slant compression plate 70.
The fluid discharged from the compression space V of the cylinder assembly 50 is discharged out of the casing C through the discharge pipe 43 of the casing C.
The compressor of the first embodiment according to the present invention will be described in views of structure, function, and reliability as s o follows.
The structure of the compressor according to the present invention can be simple because an additional balance weight for balancing the rotation is not used by installing the rotating shaft 60 and the slant compression plate 70.
In addition, a part of the rotating shaft 60 and the slant compression plate 70 which are located inside the compression space V of the cylinder assembly 50 have small volume, and therefore the dead volume is reduced and the compression space is enlarged relatively, whereby the compression efficiency can be increased.
2 o That is, when comparing the compressor according to the present invention to the rotary compressor shown in Figure 1, the dead volume is increased and the compression space is reduced because the rotating shaft 3 and the eccentric unit 3a, and the rolling piston 5 inserted into the eccentric unit 3a are located in the compression space V of the cylinder in case of the rotary compressor, however, the rotating shaft 60 and the slant compression plate 70 are located in the compression space V of the cylinder 55, and the dead volume is reduced and the compression space is increased according to the present invention, whereby the compression efficiency is increased in same cylinder compression space.
Also, according to the present invention, an additional balance weight does not needed, and therefore the torque rotating the rotating shaft 60 to which the slant compression plate 70 is coupled is reduced. Therefore, the electric consumption can be reduced, and sufficient driving force can be Zo ensured by using the motor device unit M having relatively small capacity.
In addition, the rotating shaft 60 and the slant compression plate 70 are balanced with each other, and therefore the vibration noise generated during rotation can be reduced.
That is, eccentric units are installed inside the rotary, reciprocating, and scroll compressors, and therefore the vibration noise is generated.
However, stable rotation can be made, whereby the vibration noise can be reduced.
Also, the slant compression plate 70 is rotated as dividing the cylinder compression space V into the first space V1 and the second space V2, and 2 o accordingly, compression force is pressed to the slant compression plate during the processes of compressing the fluid in the first and the second spaces V1 and V2. At that time, the generated compression force is applied to the first and the second spaces V1 and V2, at the same time, the force of a tangential component of the slanted surface on the slant compression plate 70 is applied as a repulsive power of the torque and the rotating shaft 60 of the motor device unit M. Therefore, the repulsive power applied to the rotating shaft 60 and to the slant compression plate 70 is relatively small, whereby the rotations of the rotating shaft 60 and of the slant compression plate 70 are stable.
In addition, when the rotating shaft 60 and the slant compression plate 70 are rotated, a friction surface where the rotating shaft 60 and the slant compression plate 70 are contacted to each other is relatively small comparing to that of the conventional compressor. Therefore the frictional loss Zo can be reduced, and the amount of oil consumption can be reduced.
A compressor of second embodiment according to the present invention will be described as follows with reference to Figures 11 through 14.
Figure 11 is a longitudinal cross-sectional view showing the Z5 compressor of the second embodiment according to the present invention, Figure 12 is a cut perspective view of principal parts showing the compressor of the second embodiment according to the present invention, Figures 13A
and 13B are longitudinal cross-sectional views showing the operation states of the compressor of the second embodiment according to the present 2 o invention, and Figure 14 is a status view showing the flowing of the fluid in the compressor of the second embodiment according to the present invention.
The compressor of the first embodiment uses the method that the compressor compresses and discharges once in both spaces, however, the compressor uses two-steps compression method by which discharged fluid are cooled and compressed again after one compression is completed.
The compressor of the second embodiment comprises a motor device unit M for generating the rotation force, and a compression device unit P for compressing and discharging the fluid inside the casing C, as in the compressor of the first embodiment.
The compression device unit P comprises a cylinder assembly 110 for forming a compression space V including a cylinder 111, a first bearing plate 113, and a second bearing plate 115, and the cylinder assembly 110 includes a slant compression plate 120 for dividing the compression space V into the to first space V1 and to the second space V2 and rotated by coupling to the rotating shaft 122.
In addition, a first vane 131 and a second vane 132, which are undergone reciprocating movement to opposite axial directions with each other by contacted to the both surfaces of the slant compression plate 120 and divide the respective spaces V1 and V2 into the changeable suction space and the compression space, are installed on the first bearing plate 113 and on the second bearing plate 115.
The cylinder 111 of true round ring form includes a first suction passage 102 on one side connected to,the first space V1 so as to be 2 o connected to fihe suction pipe 101 of the casing C, and a second suction passage 105 is formed as communicated in the second space V2 on the opposite side with a phase difference of 180° with the first suction passage 102.
The first bearing plate 113 includes a firsfi discharge hole 103 for discharging the firstly compressed fluid from the first space V1, and a suction passage 104 is formed on the position having phase difference of 180°
with the first discharge hole 103 for inducing the firstly compressed fluid discharged from the first discharge hole 103 through a second suction passage 105.
A first discharge valve 135 which is opened/closed according to pressure of the fluid in the first space V1 is installed on a front end part of the first discharge hole 103. The discharge valve 135 may be formed as a various shapes, a rectangular discharge valve having a retainer is used in the present Z o invention.
A second discharge hole 106 is formed toward the inner space of the casing C for discharging the fluid secondly compressed in the second space V2 The second bearing plate 115 in the second bearing plate 115, A second discharge valve 136 of same shape as the first discharge valve 135 is 25 installed on a front end part of the second discharge hole 106 so that the second discharge valve 136 can be opened/closed according to the pressure of the fluid in the second space V2.
A first discharge muffler 117 having a large area unit and a small area unit is installed on the upper surface of the first bearing plate 113 so that 2 o discharge noise of the fluid discharged from the first discharge hole 103 is reduced.
It is desirable that the first discharge muffler accepts the first discharge hole 103 and the suction passage 104 of the first bearing plate 113 so as to use these as communication members between the first and the second spaces V1 and V2, and the small area unit is located between the first discharge hole 103 and the suction passage 104.
On the other hand, a discharge hole 107 for discharging the fluid which is secondly compressed in the cylinder assembly 110 to the inside of the s casing C is formed on a second discharge muffler 119 which is located on the opposite position of the first discharge muffler 117.
The operation and effect of the compressor of the second embodiment according to the present invention will be described as follows.
When the electric current is supplied to the motor device unit M and s o the rotating shaft 122 is rotated with the slant compression plate 120, then the fluid is sucked into the first space V1 through the first suction passage 102 of the cylinder 111 and primarily compressed according to the rotation of the slant compression plate 120 as shown in Figure 14. In addition, the primarily compressed fluid pushes the first discharge valve 135 and is discharged into 15 the first discharge muffler 117 through the first discharge hole 103 of the first bearing plate 113 when the pressure of the fluid reaches to a certain degree, and then is sucked into the second space V2 through the suction passage 104 and the second suction passage 105 in the cylinder 111.
The fluid sucked into the second space V2 is secondarily compressed 2 0 by the continuous rotation of the slant compression plate 120. And then, the compressed fluid is discharged while pushing the second discharge valve 136 when the compressed fluid is reached to a certain pressure, and after that, the fluid is discharged into the casing C through the discharge hole 107 of the second discharge muffler 119.
invention and a cross-sectional view showing the line D-D, and Figure 17 is a cut perspective view of the principal parts showing the compressor of the third embodiment according to the present invention.
The compressor of the third embodiment according to the present s invention further comprises damping recesses 158a and 159a are installed in the cylinder assembly 155 so that the noise can be reduced, besides the components of the compressor of the first embodiment.
The compressor of the third embodiment comprises a motor device unit M for generating the rotation force, and a compression device unit P for s o compressing and discharging the fluid in the casing C.
The compression device unit P comprises a cylinder assembly 150 having a compression space; a rotating shaft 160 penetrating the cylinder assembly 150 from the motor device unit M; a slant compression plate 170 of sine wave form for dividing the compression space V in the cylinder z5 assembly 150 into a plurality of spaces; and a plurality of vanes 180A and 180B moving while changing the space in the compression space V into a suction space and a compression space according to the rotation of the slant compression plate 170.
The cylinder assembly 150 comprises a cylinder 150 fixed inside the 2 o casing C; and a first bearing plate 158 and a second bearing plate 159 fixed on an upper and a lower part of the cylinder and forming the compression space V with the cylinder 155.
Especially, the damping recesses 158a and 159a of round recess form having a certain depth are respectively installed on the first bearing plate The fluid discharged into the casing C is compressed twice by the repeated processes that the fluid is discharged to a refrigerating cycle through the discharge pipe 108 of the casing C going through gaps between the respective members.
As described above, the compressor of the second embodiment according to the present invention is suitable for the refrigerating cycle for air conditioning which needs high compression ratio, and load of the motor device unit M, the number of components, and the volume of the compressor can be reduced as the minimum because the fluid can be compressed twice z o in one compression device unit P.
Also, if an upper space is to be the first compression space V1 and a lower space is to be the second compression space V2 in case that the compressor described above is constructed as standing form, then the second compression space V2 has relatively high pressure and supports the s s rotating shaft 122 and the slant compression plate 120. Therefore, the axial load and the pressure of the compressor is reduced, whereby the performance of the compressor can be increased.
A compressor of a third embodiment according to the present invention 2 o will be described as follows with reference to Figures 15 through 18.
Figure 15 is a longitudinal cross-sectional view of principal parts showing the compressor of the third embodiment according to the present invention, Figures 16A and 16B are a transverse cross-sectional view showing the compressor of the third embodiment according to the present and on the second bearing plate 159 so that pressure pulsation of the first space V1 and of the second space V2.
It is desirable that the damping recesses 158a and 159a are formed to be located within 180° from the respective vanes 180A and 180B range toward the rotational direction of the slant compression plate 170, and the damping recesses may be formed on one space between the first and the second spaces V1 and V2.
On the other hand, the compressor of the third embodiment according to the present invention comprises suction passages 153A and 154B and Zo discharge passages 154A and 154B formed in the first and the second spaces V1 and V2 which are divided by the slant compression plate 170, same as in the compressor of the first embodiment according to the present invention.
In addition, vanes 180A and 180B are located respectively between the suction passages 153A and 153B, and the discharge passages 154A and 154B, and the discharge passages 154A and 154B are opened/closed by discharge valves 190A and 190B.
Figures 18A and 18B are cross-sectional views of principal parts showing modified embodiments of the damping recesses in the compressor of the third embodiment according to the present invention.
As shown in Figure 18A, the damping recess 158a' may be formed as an oval, and as shown in Figure 18B, the damping recess 158a" may be formed as two recesses having different inner diameters and stepped inside.
As described above, the damping recess can be modified its shape, size, and number according to the capacity and the condition of the compressor.
The operation and effect of the compressor of the third embodiment according to the present invention will be described as follows.
When the rotating shaft 160 and the slant compression plate 170 are rotated inside the compression space V of the cylinder assembly 150 according to the operation of the motor device unit M, then the first space V1 and the second space V2 are changed into the suction space and the compression space centering around the vanes 180A and 180B. And the fluid 1 o is sucked and compressed through the suction passages 153A and 153B, and the compressed fluid is discharged into the casing C through the discharge passages 154A and 154B.
As described above, in the processes that the fluid is sucked, compressed, and discharged in the first and the second spaces V1 and V2 by the volume change in the first and the second spaces V1 and V2 of the cylinder assembly 150, the pressure pulsation is generated by the pressure change of the fluid. And the pressure pulsation is sucked by the damping recesses 158a and 159a formed in the first and the second spaces V1 and V2.
2 o Therefore, according to the compressor of the third embodiment, the pressure pulsation generated by the pressure change of the fluid is sucked through the damping recesses 158a and 159a, in the processes of sucking, compressing, and discharging the fluid in high temperature and pressure by the rotation of the slant compression plate 170, whereby the noise generated by the pressure pulsation can be reduced.
A compressor of a fourth embodiment according to the present invention will be described as follows with reference to Figures 19 through 21.
s Figure 19 is a longitudinal cross-sectional view and an enlarged view showing the compressor of the fourth embodiment according to the present invention, and Figure 20 is a transverse cross-sectional view and an enlarged view showing the compressor of the fourth embodiment according to the present invention.
1o The compressor of the fourth embodiment according to the present invention comprises damping recesses so as to reduce the pulsation noise as in the compressor of the third embodiment, however the damping recesses are formed on the inner circumferential surface of a cylinder 155' unlike the damping recesses in the compressor of the third embodiment.
15 The compressor of the fourth embodiment comprises a motor device unit M for generating the rotation force and a compression device unit P for compressing and discharging the fluid inside the casing C, and the compression device unit P comprises a cylinder assembly 150', a rotating shaft 160', a slant compression plate 170', and a plurality of vanes 180A' and 20 180B'.
A cylinder 155', a first bearing plate 158', and a second bearing plate 159' are assembled inside the cylinder assembly 150', and therefore a compression space V is formed.
Suction passages 153A' and 153B' respectively communicated with the compression space V are formed to have a phase difFerence of 180°
with each other on the cylinder 155'. In addition, the suction passage 153A' of the first space V1 is formed on an upper part of the cylinder 155', and the suction passage 1538' of the second space V2 is formed on a lower part of the s cylinder 155'.
The suction passages 153A' and 1538' of the first and the second spaces V1 and V2 are formed on positions apart a certain disfiance from the upper and the lower surfaces of the cylinder 155' which are contacted to the first and the second bearing plates 158' and 159'.
to In addition, the slant compression plate 170' is formed to have thicknesses on the upper and lower dead centers can open/close the suction passage 153A' of the first space and the suction passage 1538' of the second space.
Especially, the damping recesses 155A and 1558 are formed between 15 the suction passages 153A' and 1538', and the first and second bearing plate 158' and 159' of the first and second spaces in the cylinder 155' so as to suck the pressure pulsation.
That is, the damping recesses 155A and 1558 are penefiratingly formed from upper or lower sides of the suction passages 153A' and 1538' 2 0 of the first and the second spaces to contacted positions with the first and second bearing plate 158' and 159', and are opened toward the inner circumferential surfaces of the cylinder 155'.
The damping recesses 155A and 1558 as described above are formed as semicircle on the inner circumferential surface of the cylinder 155' as shown in Figure 20 and opened toward the compression space V of the cylinder 155', and the size of the opened part k is same as the diameter of the semicircle.
In addition, it is desirable that the inner diameters of the semicircle of the damping recesses 155A and 155B are formed to be smaller than those of the suction passages 153A' and 153B'.
On the other hand, discharge passages 154A' and 154B' are located on the first and the second bearing plate 158' and 159' so that the fluid compressed inside the first and the second spaces V1 and V2 can be to discharged therethrough.
Figures 21 A, 21 B, and 21 C are detailed cross-sectional views of principal parts showing modified embodiments of the damping recesses in the compressor of the fourth embodiment according to the present invention.
The damping recess 155C shown in Figure 21A is formed by s s overlapping relatively large semicircle and a relatively small circle, and at that time, the small circle is located inward.
And the damping recess 155D shown in Figure 21 B is formed as a circle similar with the damping recess 155A shown in Figure 20, and the size of the opened part toward the compression space is smaller than that of the 2 o damping recess 155A. That is, size of the opened part of the damping recess 155D is smaller than the diameter of the circle.
In addition, the damping recess 155E shown in Figure 21C is formed same as the damping recess 155D in Figure 21 B, however it is installed on a position moved to one side from the center line of the suction passage 153E.
That is, the damping recess 155E is located to have a center point on the position where is not overlapped with the center line of the suction passage 153E.
The operation and efFect of the compressor of the fourth embodiment according to the present invention will be described as follows.
In the compressor of the fourth embodiment according to the present invention, the pressure pulsation caused by the pressure change of the fluid is also generated during the processes of sucking, compressing, and so discharging the fluid in the first and the second spaces V1 and V2 by the volume change of the first and the second spaces V1 and V2 of the cylinder assembly 150', and the.pressure pulsation is sucked by the damping recesses 155A and 155B formed on inner circumferential surface of the cylinder 155' in the first and the second spaces V1 and V2.
That is, the damping recesses 155A and 155B can suck the pressure pulsation of a certain frequency range by changing the inner volume.
The compressor of the fourth embodiment according to the present invention comprises the damping recesses 155a and 155B which suck the pressure pulsation generated by the pressure change of the fluid in the 2 o processes of sucking, compressing, and discharging the fluid while the rotation of the slant compression plate 170', whereby the vibration and noise generated by the pressure pulsation can be reduced and the reliability of the compressor can be increased.
A compressor of a fifth embodiment according to the present invention will be described as follows with reference to Figures 22 through 24.
Figure 22 is a longitudinal cross-sectional view of principal parts showing the compressor of the fifth embodiment according to the present invention, Figure 23 is a cut perspective view showing the compressor of the fifth embodiment according to the present invention, and Figure 24 is a transverse cross-sectional view showing the compressor of the fifth embodiment according to the present invention.
The discharge passages are formed on the first and the second so bearing plate in the compressor of the first embodiment, however discharge passages 205 and 206 are formed penetrating a cylinder 211 in the compressor of the fifth embodiment according to the present invention.
The compressor of the fifth embodiment according to the present invention comprises a casing C, a motor device unit M, and a compression 15 device unit P, and the compression device unit P comprises a cylinder assembly 210, a slant compression plate 220, and a first vane 231 and a second vane 232.
A cylinder 211, a first bearing plate 213, and a second bearing plate 215 are assembled in the cylinder assembly 210, whereby a compression 2 o space V is formed.
A first suction passage 202 is connected to the first space V1 inside the cylinder 211 so as to be connected to the suction pipe 201 in the casing C, and a suction passage 203 connected to another suction pipe(not shown) is communicatively formed in the second space V2 having a phase difference of Z 80° with the first suction passage 202 on the opposite side.
Especially, discharge recess units 211 a and 211 b which are emitted parts having a phase difference of 180° are formed on both sides of the outer circumferential surFace of the cylinder 211, and the discharge passage 205 and 206 are formed on the discharge recess units 211 a and 211 b so that the fluid compressed in the compression space V can be discharged.
In addition, discharge valves 235 and 236 opening/closing the discharge passages 205 and 206 are installed by a bolt inside the discharge recess units 211 a and 211 b, and an engraved recess 211 d having a certain 1 o depth is formed inside the discharge recess units 211 a and 211 b so that the discharge valves can be mounted as shown in Figure 24.
Vanes 231 and 232 are respectively located between the suction passages 202 and 203, and the discharge passages 205 and 206 in the compressor of the fifth embodiment according to the present invention.
The operation of the compressor of the fifth embodiment according to the present invention will be described as follows.
When the rotating shaft 222 and the slant compression plate 220 are rotated inside the compression space V of the cylinder assembly 210 in accordance with the operation of the motor device unit M, then the first space 2 o V1 and fihe second space V2 are respectively changed into the suction space and compression space centering around the respective vane 231 and 232.
Then the fluid is sucked from the suction passages 202 and 203, and compressed. In addition, the compressed fluid is discharged into the casing C through the discharge passage 205 and 206 formed in the cylinder 211 while opening the discharge valves 235 and 236.
A compressor of a sixth embodiment according to the present invention will be described as follows with reference to Figures 25 through 27.
Figure 25 is a cut perspective view of principal parts showing the compressor of the sixth embodiment according to the present invention, and Figure 26 is a transverse cross-sectional view and a detailed view showing the compressor of the sixth embodiment according to the present invention.
Structure of the compressor of the sixth embodiment according to the Zo present invention is similar with that of the compressor of the fifth embodiment, however flowing resistance reducing units 205a and 206a are formed on inlet unit of discharge passages 205' and 206' so that the flowing resistance can be reduced when the compressed fluid is discharged in a cylinder assembly 210'.
15 Descriptions for the same components as those of the fifth embodiment will be omitted.
Two discharge passages 205' and 206' having a phase difference of 180° with each other are formed toward the discharge recess units 211 a' and 219 b' from the compression space V of the cylinder assembly 210' in the 2 o compressor.
The flowing resistance reducing units 205a and 206a which are omitted parts are formed on inlet side the discharge passages 205' and 206' , that is, the compression space V of the cylinder 211 so that the flowing resistance generated when the compressed fluid is discharged.
That is, the discharge passages 205' and 206' are formed as straight lines so as to face the center direction of the compression space V. The flowing resistance units 205a and 206a are formed so that the sizes of the inlet parts of the discharge passages 205' and 206' are larger than those of the outlet parts, and these are slanted so that the size is reduced gradually from the inlet part to the outlet part.
The flowing resistance reducing units 205a and 206a are formed so as to face counterpart direction of rotation of the slant compression plate 220'.
Figures 27A and 27B are detailed cross-sectional views of principal o parts showing modified embodiments of the flowing resistance reducing units in the compressor of the sixth embodiment according to the present invention.
The flowing resistance reducing unit 206c which is narrowed toward the outlet part shown in Figure 27A is formed as a recess having a plurality of steps and having a certain depth.
The flowing resistance reducing unit 206d is formed same as the flowing resistance reducing unit shown in Figure 26, and is slanted so as to be reduced its size toward the outlet part of the discharge passage 206'.
However, the discharge passage 206' is formed as slanted a certain angle 8 against the center direction of the compression space V in the 2 o cylinder 211'.
The operation and effiect of the compressor of the sixth embodiment according to the present invention will be described as follows.
When the slant compression plate 220' is rotated according to operation of the motor device unit M and the upper dead center reaches a position of 210° from the vanes 231' and 232', the discharge valves 235' and 236' are opened and the compressed fluid is discharged into the casing C
through the discharge passages 205' and 206' in which the flowing resistance reducing units 205a and 206a are formed, with reference to Figures 25 and 26.
At that time, a smooth passage without protruded part is formed by the flowing resistance reducing unit when the compressed fluid flows into the discharge passages 205' and 206' inside the compression space V, whereby the flowing resistance of the fluid is reduced.
so Also, the flowing resistance reducing units 205a and 206a funcfiion as resonator for reducing the operation noise of the discharge valves 235' and 236', whereby the noise is reduced and over-compression is prevented.
A compressor of a seventh embodiment according to the present s5 invention will be described as follows with reference to Figures 28 through 31.
Figure 28 is a longitudinal view showing principal parts of the compressor of the seventh embodiment according to the present invention, Figure 29 is a detailed cross-sectional view of line E-E in Figure 28, Figure 30 is a transverse cross-sectional view showing the compressor of the 2 o seventh embodiment according to the present invention, and Figure 31 is a cut perspective view showing the principal parts of the compressor of the seventh embodiment according to the present invention, In the compressor of the seventh embodiment according to the present invention, the adhering structure of the upper dead center R1 and the lower dead center R2 on the slant compression plate 270 is changed so that a leakage of the fluid in the space of high pressure toward the space of lower pressure can be prevented.
The compressor of the seventh embodiment comprises the casing C, the motor device unit M, and the compression device unit P as in the compressor of the first embodiment, and the compression device unit P
comprises a cylinder assembly 250, a rotating shaft 260 and a slant compression plate 270, and a first vane 281 and a second vane 282.
The slant compression plate 270 of ring round disc shape is formed so as a sine wave having the upper dead center R1 and the lower dead center R2 with a phase difference of 180°, and outer circumferential surface of the slant compression plate 270 is formed as a true circle when projected from plane so as to be sildingly contacted to inner circumferential surface of the cylinder 255.
In addition, the upper dead cenfier R1 is always slidingly contacted to a bottom surface of the first bearing plate 256, however the lower dead center R2 is located to be slidingly contacted to an upper surface of the second bearing plate 257 always.
Especially, the slant compression plate 270 is formed as a plane 2 o surface having a certain area so that the upper dead center R1 and the lower dead center R2 are respectively surface contacted to the first and to the second bearing plates 256 and 257.
The slant compression plate 270 may be formed such that the parts on which the upper dead center R1 and the lower dead center R2 are located are cut to be a plane, or may be formed as adding the thickness around the upper dead center R1 and the lower dead center R2 in order to form the plane upper and lower dead centers R1 and R2.
Therefore, the slant compression plate 270 divides the compression space V inside the cylinder assembly 250 into the first and the second spaces V1 and V2 in longitudinal direction, and the plane upper and lower dead centers R1 and R2 divide the respective spaces into the suction space and the discharge space.
The operation and effect of the compressor in the seventh embodiment to according to the present invention will be described as follows.
When the motor device unit M is operated, the rotating shaft 260 and the slant compression plate 270 are rotated inside the cylinder assembly 250.
In addition, the suction, compression, and discharging operations of the fluid are made in the first and the second spaces V1 and V2 according to the z5 rotation of the slant compression plate 270.
Herein, the upper and lower dead centers R1 and R2 are formed as planes, are contacted surfaces to the first and the second bearing plates 256 and 257, and compress the fluid in the first and second spaces V1 and V2, whereby the leakage of the fluid compressed in the compression spaces V1 p 2 o and V2p toward the suction spaces V1 s and V2s can be prevented.
As described above, in the compressor in the seventh embodiment according to the present invention, the contacted area of the slant compression plate 270 and the first and second bearing plates 256 and 257 is increased, and therefore the leakage of the fluid in the compression spaces V1p and V2p to the suction spaces V1s and V2s during compressing the fluid can be reduced, whereby the compression efficiency of the compressor can be increased.
A compressor in an eighth embodiment according to the present invention will be described as follows with reference to Figures 32 through 34.
Figure 32 is a cut perspective view showing principal parts of the compressor in the eighth embodiment according to the present invention, Figure 33 is a longitudinal cross-sectional view showing the compressor of s o the eighth embodiment according to the present invention, and Figure 34 is a detailed cross-sectional view showing the line F-F in Figure 33.
The compressor in the eighth embodiment according to the present invention is constructed such that a labyrinth seal 311 is formed on outer circumferential surface of a slant compression plate 310 and therefore the 15 leakage of compressed fluid between inner circumferential surface of a cylinder 302 and outer circumferential surface of the slant compression plate 310 can be reduced.
That is, the slant compression plate 310 is connected to a rotating shaft 304 in the compression space V of the cylinder 302, and the outer 2 o circumferential surface of the slant compression plate 310 is slidingly contacted to the inner circumferential surface of the cylinder 302. In addition, the slant compression plate 310 divides the compression space V in the cylinder 302 into the first and the second spaces V1 and V2. And a labyrinth seal 311 having one or more recess of band shape is formed on the outer circumferential surface of the slant compression plate 310 so as to prevent the leakage of the compressed fluid.
The shape of cross-section of the labyrinth seal 311 may be formed as a square, as a triangle form(not shown), or as a circular arc(not shown) s when projected from the front side.
Components besides the slant compression plate 310 are similar with those on the first embodiment, and therefore detailed descriptions are omitted.
The operation and effect of the compressor in the eighth embodiment so according to the present invention will be described as follows.
When the slant compression plate 310 is rotated inside the compression space V in the cylinder 302, the first and the second spaces V1 and V2 are divided into the suction spaces V1 s and V2s and the compression spaces V1 p and V2p centering around both vanes 321 and 322, and around 15 the upper and lower dead centers R1 and R2 on the slant compression plate 310.
At that time, the compression space V2p of the second space V2 is located on the lower part of the suction space V1 s of the first space V2, and the suction space V2s of the second space V2 is located on the lower part of 2 o the first space V1 centering around the slant compression plate 310.
That is, one side of the first and the second spaces V1 and V2 becomes the compression space of high pressure, and the other side becomes the suction space of relatively low pressure making the slant compression plate 310 a border.
Therefore, when the fluid pressure in the first space V1 becomes relatively high pressure comparing to that in the second space V2, a part of the fluid in the first space V1 is likely to leak to the second space V2 through the gap between the outer circumferential surface of the slant compression plate 310 and the inner circumferential surface of the cylinder 302.
At that time, the Labyrinth seal 311 is formed on the outer circumferential surface of the slant compression plate 310, and therefore the labyrinth seat reduces the pressure of the fluid which is likely to leak through the gap between the outer circumferential surface of the slant compression Z o plate and the inner circumferential surface of the cylinder 302.
Therefore, the labyrinth seal can prevent the leakage of the fluid from the high pressure space to the lower pressure space.
According to the compressor in the eighth embodiment, the labyrinth seal 311 is formed on the outer circumferential surface of the slant Zs compression plate 310 and minimize the leakage of the fluid from the compression space to the suction space through the gap between the inner circumferential surface of the cylinder 302 and the outer circumferential surface of the slant compression plate 310, whereby the compression efficiency can be increased.
A compressor in a ninth embodiment according to the present invenfiion will be described as follows with reference to Figures 35 through 37.
Figure 35 is a longitudinal cross-sectional view showing principal parts of the compressor in the ninth embodiment according to the present invenfiion, Figure 36 is a cut perspective view showing the principal parts of the compressor in the ninth embodiment according to the present invention, and Figure 37 is a detailed view showing the principal parts of the compressor in the ninth embodiment according to the present invention.
The compressor in the ninth embodiment according to the present invention is constructed such that vanes 481 and 482 can be undergo reciprocating movements smoothly irrespective of around components inside the compression space ~/ of a cylinder assembly 455.
The compressor of the ninth embodiment according to the present Zo invention comprises the casing C, the motor device unit M, and the compression device unit P as in the compressor of the first embodiment, and the compression device unit P comprises a cylinder assembly 450, a rotating shaft 460 and a slant compression plate 470, and a first vane 481 and a second vane 482.
In the cylinder assembly 450, a first bearing plate 430 and a second bearing plate 440 are assembled on an upper side and on a lower side centering around a cylinder 455, and thereby the compression space V is formed therein.
On the first and the second bearing plates 430 and 440, shaft units 2 0 431 and 441 in which the rotating shaft 460 is inserted into center part are formed, and vane slots 433 and 443 having a phase difference of 180° in vertical direction are respectively formed on side surfaces of the shaft units 431 and 441.
Especially, protruded coupling units 435 and 445 of circular shapes, which are protruded inward of the compression space V as a certain height, having outer diameters corresponding to the inner diameter of the cylinder 455 are formed on the first and the second bearing plates 430 and 440.
A hub unit 465 is formed inside the compression space V of the s cylinder assembly 450 so that the slant compression plate 470 can be installed around the rotating shaft 460, and hub coupling recesses 437 and 447 are formed on the first and the second bearing plates 430 and 440 so that upper and lower end parts of the hub unit 465 are inserted into the center part of the protruded coupling units 435 and 445.
z o On the other hand, the slant compression plate 470 is a curved plate of sine wave form on which the upper dead center R1 and the lower dead center R2 are located with a phase difference of 180°. The upper and the lower dead centers R1 and R2 are respectively contacted to the lower and the upper surfaces of the protruded coupling units 435 and 445 and rotated.
15 Also, a plurality of suction passages 456 and 457 are formed on the cylinder 455 through which the fluid is sucked into the compression space V, and the suction passages 456 and 456 are penetratingly formed on positions apart a certain distance from the upper surface and from the bottom surface of the cylinder 455 so as to be located on the lower or the upper side of the 2 o protruded coupling units 435 and 445.
The operation and effect of the compressor in the ninth embodiment according to the present invention will be described as follows.
Three surfaces on frame of the vanes 481 and 482 are contacted respectively to the inner circumferential surface of the cylinder 455, to upper or lower surface of the slant compression plate 470, and to the outer circumferential surface of the hub unit 465 of the rotating unit 460 in the state of being inserted to vane slots 433 and 443, and the vanes are undergone linear reciprocating movement in vertical direction according to the rotation of the slant compression plate 470.
At that time, distance of the reciprocating movement of the vanes 481 and 482 is limited between the bottom surface of the first bearing plate 430 and the upper surface of the protruded coupling unit 445 of the second bearing plate 440.
s o Therefore, front ends of the vanes 481 and 482 are undergone the linear reciprocating movement only inside the compression space V of the cylinder assembly 450, and therefore the front ends of the vanes 481 and 482 are not interrupted by the upper or lower end part of the cylinder 455, and by the upper or lower end part of the hub unit 465, whereby the vanes 481 and 15 482 are able to be undergone smooth reciprocating movement.
Also, the protruded coupling parts 435 and 445 of the first and second bearing plate 430 and 440 are inserted into the compression space V of the cylinder 455, and therefore the positions of the compression space V of the vane slots 433 and 443 and the cylinder 455 are fitted correctly, whereby the 2 o wrong operation of the vanes 430 and 440 caused by the assembling margin can be prevented.
A compressor of a tenth embodiment according to the present invention will be described as follows with reference to Figures 38 through 42.
4s Figure 38 is a longitudinal cross-sectional view showing the compressor in the tenth embodiment, Figure 39 is a transverse cross-sectional view showing principal parts of the compressor in the tenth embodiment according to the present invention, and Figure 40 is a cut ~ perspective view showing the principal parts ofi the compressor in the tenth embodiment according to the present invention.
The compressor of the tenth embodiment according to the present invention is constructed to locate vanes 581 and 582 which are located on both sides of a slant compression plate 570 on same vertical surface.
to The compressor of the tenth embodiment according to the present invention comprises a casing C, a motor device unit M, a compression device unit P, and the compression device unit P comprises a cylinder assembly, a rotafiing shaft 560 and a slant compression plate 570, and a first vane 581 and a second vane 582.
15 A first bearing plate -530 and a second bearing plate 540 are assembled centering around a cylinder 555 on an upper and on a lower side inside the cylinder assembly 550, whereby a compression space V is formed inside.
Herein, a vane slot 531 is formed on the first bearing plate 530 so that 2 o the first vane 581 is inserted and undergone reciprocating movement, and a vane slot 541 is formed on same position of the second bearing plate 540 in vertical direction of the vane slot 531 of the first bearing plate 530.
That is, the vane slot on the first bearing plate 530 and the vane slot 540 on the second bearing plate 540 are formed to be located on same plane as each other.
In addition, a suction passage 556 and discharge passages 557 and 558 are respectively formed on the cylinder 555, the discharge passages 557 and 558 are penetratingly formed from the compression space V of the cylinder assembly 550 to a discharge recess 559 formed on one side of the cylinder 555 as shown in Figure 40. At that time, the first discharge passage 557 and the second discharge passage 558 are formed in a row in vertical direction.
Herein, it is desirable that the discharge passages 557 and 558 are Zo respectively formed on the upper end part and the lower end part of the cylinder 55 so that the compressed fluid in the first and the second spaces V1 and V2, and that the size of the discharge passage is smaller than thickness of the slant compression plate 570.
In addition, discharge valves 591 and 592 for openinglclosing the discharge passages 557 and 558 are installed on the discharge recess 559.
And the suction passage 556 is located on opposite position of the first and the second discharge 557 and 558 centering around the two vanes 581 and 582.
The first and second vanes 581 and 582 are located on same vertical 2o surface centering around the slant compression plate 570, and the suction passage 556 and the discharge passages 557 and 558 are located on both sides of the vanes 581 and 582.
Herein, the first and second vanes 581 and 582 are located to be overlapped with some parts of the first and second discharge passages 557 and 558.
In addition, springs 583 and 584 are respectively located behind the first and second vanes 581 and 582 so that the two vanes 581 and 582 are adhered to the slant compression plate 570, and the springs are supported by spring retainers 585 and 586 which are fixed on the first and second bearing plates 530 and 540.
The operation and effect of the compressor in the tenth embodiment according to the present invention will be described as follows.
When the motor device unit M is operated, the rotating shaft 560 and 1o the slant compression plate 570 inside the cylinder assembly 550 are rotated.
At that time, the slant compression plate 570 is rotated inside the compression space V of the cylinder assembly 550, and accordingly divides and changes the respective spaces of the first and second spaces V1 and V2 into the suction spaces V1 s and V2s and compression spaces V1 p and V2p.
And the fluid is sucked, compressed, and discharged through the suction passage 556 and through the discharge passages 557 and 558.
Herein, the operation of the compressor in the tenth embodiment will be described as follows with reference to Figures 41 and 42.
Figure 41 is a transverse cross-sectional view showing principal parts 2 o for describing the compression processes of the compressor in the tenth embodiment, and Figures 42A, 42B, 42C, and 42D are longitudinal cross-secfiional views showing the compression processes of the compressor in the tenth embodiment according to the present invention.
With reference to Figures 41 and 42, when the upper dead center R1 of the slant compression plate 570 is located on a position P3 between the vanes 581 and 582, then the discharge of the compressed fluid in the first space V1 is completed, and suction and compression of the fluid are processing in the second space V2. At that time, the first vane 581 reaches to highest position, and the second vane 582 also reaches to the highest position.
After that, when the upper dead center R1 of the slant compression plate 570 reaches to a position P4 which is 45° from the first and second vanes 581 and 582, the suction of the fluid is started in the first space V1 and Zo at the same time the compression of the sucked fluid is started. And in the second space V2, the discharge of the compressed fluid becomes completed and at the same time the suction of the fluid is completed.
At that time, the first and second vanes 581 and 582 are located on intermediate position in the compression space V by lowering.
After that, the upper dead center R1 of the slant compression plate 570 reaches to a position P5 of 180° from the first and second vanes 581 and 582 as shown in Figures 41 and 42C, the suction of fluid and the compression of the sucked fluid are processed at the same time in the first space V1, and the discharge of the compressed fluid and the suction of fluid are already 2 o completed in the second space V2.
At that time, the first and second vanes 581 and 582 are located on lowest position in lower part.
After that, the upper dead center R1 of the slant compression plate 570 reaches to a position P6 of 135° from the first and second vanes 581 and 582 as shown in Figures 41 and 42D, the discharge of the compressed fluid and the suction of the fluid are almost completed in the first space V1, and the suction of the fluid is started and the compression of the sucked fluid is processed in the second space V2.
At that time, the first and second vanes 581 and 582 are located on intermediate part of the compression space V by lowering.
As the processes above are repeated, the fluid is sucked, compressed, and discharge into the first and second spaces V1 and V2. And the processes 2 o in the first and second spaces V1 and V2 are not performed at that same time, and performed with a phase difference of 180°.
That is, the discharge of the fluid is made with the phase difference of 180° in the first and second spaces V1 and V2. The discharge fluid from the cylinder assembly as described above is discharged out of the casing C
through the discharge pipe 510 as shown in Figure 38.
According to the compressor of the tenth embodiment, the fluid of high pressure and high temperature compressed respectively inside the first and second spaces V1 and V2 is discharged having phase difference with each other according to the rotation of the rotating shaft 560, and therefore the fluid 2 o is gradually discharged and the pressure pulsation caused by the discharged fluid is reduced.
Also, the processes of the sucking, compressing, and discharging the fluid in the first and second spaces V1 and V2 are processed with different phases with each other, and therefore load torque applied to the motor device unit M is reduced as half of that in case of processing with same phases.
Also, a rotating body having a rotator 561 and the rotating shaft 560 in the motor device unit M is balanced in rotation, and therefore the stable driving is made without the unbalancing of the rotation. In addition, volume which is occupied by the components located in the compression space V of the cylinder assembly 550, that is, the dead volume is reduced, whereby the compression efficiency is increased.
so A compressor of an eleventh embodiment according to the present invention will be described as follows with reference to Figures 43 and 44.
Figure 43 is a longitudinal cross-sectional view showing the compressor in the eleventh embodiment, and Figures 44A and 44B are detailed cross-sectional views of principal parts showing the operation state Of a vane in the eleventh embodiment according to the present invention.
The compressor in the eleventh embodiment according to the present invention comprises two vanes 681 and 682 located on same vertical surface as in the compressor of the tenth embodiment, however a coil spring 685 for supplying an elastic force to the vanes 681 and 682 is constructed as one.
2 o Herein, descriptions for same components as those of the tenth embodiment will be omitted.
In the compressor of the eleventh embodiment according to the present invention, the first and second vanes 681 and 682 are located on the same plane in vane slots 631 and 641 of first and second bearing plates 630 and 640 centering around a slant compression plate 670.
Herein, the first and second vanes 681 and 682 are supplied the elastic force by one elastic connecting member.
The elastic connecting member comprises a first connecting member 683 coupled to the first vane 681, a second connecting member 684 coupled to the second vane 682, and a coil spring 685 connecting the first connecting member 683 and the second connecting member 684.
The first and second connecting members 683 and 684 of rod or plate form having a certain length are coupled behind the first and second vanes s o 681 and 682 respectively.
The coil spring 685 is inserted into the first and second bearing plates 630 and 640 and into spring penetrating holes 633, 643, and 659 penetrating the cylinder 655, and both ends of the coil spring 685 are coupled to the first and second connecting members 684 respectively.
The operation and effect of the compressor in the eleventh embodiment according to the present invention will be described as follows.
The first and second vanes 681 and 682 are moved up and down in accordance with the movement of the slant compression plate 670 in the state that the first and second vanes are respectively contacted to upper and lower 2 o surfaces of the slant compression plate 670 by the elastic force of the coil spring 685.
That is, as shown in Figure 44A, when the upper dead center R1 of the slant compression plate 670 is located on the first and second vanes 681 and 682, the first and second vanes 681 and 682 are adhered to both surfaces of the slant compression plate 670 with a certain force by the elastic force of the coil spring 685, and the first and second vanes 681 and 682 and the coil spring 685 are moved upward.
After that, as shown in Figure 44B, when the slant compression plate 670 is rotated and the lower dead center R2 of the slant compression plate 670 is located on the positions of the first and second vanes 681 and 682, the first and second vanes 681 and 682 are adhered to both surfaces of the slant compression plate 670 by the elastic force of the coil spring 685 with a certain force, and the first and second vanes 681 and 682 and the coil spring 685 are z o moved downward.
As described above, the first and second vanes 681 and 682 and the coil spring 685 are moved up and down together along with the curved surface of the slant compression plate 670 in accordance with the rotation of the slant compression plate 670, and changes the first and second spaces V1 and V2 into the suction space and the compression space.
At that time, the coil spring 685 makes the first and second vanes 681 and 682 be adhered to the slant compression plate 670 with a certain force by set elastic force without distortion of tension or contraction.
Therefore, in the compressor in the eleventh embodiment according 2 o to the present invention, the first and second vanes 681 and 682 are adhered to the slant compression plate 670 with a certain adhering force, and therefore the sealing force of the first and second spaces in which the fluid is sucked and compressed is increased, whereby the compression efficiency is increased. In addition, the structure is simple and the number of the components is small, whereby the production cost can be reduced.
A compressor of a twelfth embodiment according to the present invention will be described as follows with reference to Figures 45 through 50.
Figure 45 is a longitudinal cross-sectional view showing principal parts of the compressor in the twelfth embodiment, Figure 46 is a cut perspective view showing the principal parts of the compressor in the twelfth embodiment, and Figures 47A, 47B, and 47C are a front view, a side view, and an enlarged perspective view showing the structure of a vane in tile compressor of the 2o twelfth embodiment according to the present invention.
The compressor of the twelfth embodiment according to the present invention is constructed so that leakage of fluid from a contacted part of a slant compression plate 730 and vanes 760 and 770 during processes of compressing the fluid can be minimized by improving the structure of the s5 vanes 760 and 770.
Descriptions for same components as those in the first embodiment of the present invention are omitted.
The vanes 760 and 770 included in the compressor of the twelfth embodiment according to the present invention are contacted to the slant 2 o compression plate 730 in the compression space inside a cylinder assembly, and a contacted part T of the vanes 760 and 770 is formed so that a curvature of the contacted part T is gradually enlarged from the rotating center of the slant compression plate 730 toward the outer circumferential surface.
That is, a shown in Figures 47A and 47B, the vanes 760 and 770 are made to have a first curved part f which is contacted to center part of the slant compression plate 730, that is, a rotating shaft 720 side; a second curved part a which is contacted to the outer circumferential surface of the slant compression plate 730, that is, to the inner circumferential surFace of a cylinder 715; and a contact curved part g which is a part connected between the first curved part f and the second curved part e. A radius of curvature of the vanes 760 and 770 is gradually enlarged from the first curved part f to the second curved part e.
Also, the contact curved part g of the vanes 760 and 770 becomes an s o entire curvature by connecting curves in which the radiuses of curvature are gradually increased from center line c of the vanes 760 and 770 in vertical direction, as shown in Figure 47C.
That is, the contact curved part g is formed such that shape of section when cut from a certain position in vertical direction of the vanes 760 and Z5 is a curvature by connecting tangent lines of circles, in which radiuses of curvature are gradually increased from the center line c centering around the center line c.
In addition, a lower end line h which is a center of the contact curved part g is a straight line making a right angle with both side surfaces d and d' 2 0 of the vanes 760 and 770, and a connecting line k which is connecting ends of fihe first curved part f and ends of the second curved part d is formed to be slanted against the lower end line h.
The vanes 760 and 770 as described above are respectively inserted into slots formed on the cylinder assembly 710. Therefore, the contacted part T is contacted to the slant compression plate 730, and the both side surfaces d and d' are respectively contacted to a hub unit of the rotating shaft 720 and to inner circumferential wall of the cylinder 715.
The operation and effect of the compressor in the twelfth embodiment according to the present invention will be described as follows.
Figures 48A and 48B are plane views showing operating states of the compressor in the twelfth embodiment, Figure 49 is a plane view showing contacting state of the vane in accordance with the rotation of the slant compression plate in the compressor of the twelfth embodiment, and figure 50 is a detailed view of the principal parts showing contacting state of the slant compression plate and the vane in the compressor of the twelfth embodiment according to the present invention.
When the upper dead center R1 of the slant compression plate 730 is contacted to the first vane 760 located in the first space V1 and the lower dead center R2 of the slant compression plate 730 is contacted to the second vane 770 located in the second space V2 as shown in Figure 48A, the discharge of compressed fluid and the suction of fluid are completed in the first and second spaces V1 and V2.
At that time, the lower end line h of the vanes 760 and 770 are 2 o accorded respectively with the upper and lower dead centers R1 and R2 of the slant compression plate 730, whereby a sealing line is made.
After that, as shown in Figure 48B, when the upper dead center R1 of the slant compression plate 730 is contacted to the second vane 770 passing through a suction passage 711 of the first space V1 by the rotating shaft 720, and the lower dead center R2 is contacted to the first vane 760 passing through the suction passage 711 of the second space V2, then the compression of fluid sucked in the first and second spaces V1 and V2 respectively is processed, and at the same time, the fluid is sucked.
s Herein, when the first and second vanes 760 and 770 are contacted to the sine wave between the upper and lower dead centers of the slant compression plate 730, the contact line which is contacted to the slant compression plate 730 is changed according the rotation angle of the slant compression plate 730, as shown in Figure 49.
so At that time, the contacted part T, that is, a part including the first and second curved parts f and a and the contact curved part g, on which the vanes 760 and 770 and the slant compression plate 730 are contacted, is formed to correspond to the thickness of the first and second vanes 760 and 770 and to the difference between the curvatures of an upper curve a and a 15 lower curve b, whereby a gap between the slant compression plate 730 and the first and second vanes 760 and 770 can be minimized.
That is, as shown in Figure 50, when the vanes 760 and 770 are located within the range of waveform curved surface of the slant compression plate 730, that is from the front end of the lower dead center R2 to the front 2o end of the upper dead center R1, a contact line, on which the contact curved part g on one side of the vane and the waveform curved surface of the slant compression plate 730 are contacted, is made. In addition, when the vanes 760 and 770 are located within a range of waveform curved surface of the slant compression plate 730, that is from the front end of the upper dead center R1 to the front end of the lower dead center R2, then a contact line, on which the contact curved part g on the other side of the vane and the waveform curved surface of the slant compression plate 730 are contacted, is made.
As described above, the slant compression plate 730 is rotated inside the compression space V of the cylinder assembly 710 by the rotation of the rotating shaft 720, and at the same time, the vanes 760 and 770 contacted to the slant compression plate 730 are moved together, whereby the fluid is sucked, compressed, and discharged continuously.
1o In the first curved part f and the second curved part a of the vanes 760 and 770 located on the sides of outer curve b and of inner curve a of the slant compression plate, and the contact curved surface part g connecting the first and second curved parts f and e, the curvature on the side of the first curved part f is smaller than that of the second curved part e, as in the outer curve 15 b having large curvature than that of the inner curve a of the slant compression plate 730. Therefore, the gap between the slant compression plate 730 and the vanes 760 and 770 for dividing and changing the suction space of lower pressure and the compression space of higher pressure can be minimized.
2 o As described above, as shown in Figure 50, the contacted part of the vanes 760 and 770, which makes the sealing with the slant compression plate 730 by contacting the slant compression plate 730, is formed to be corresponded to the thickness of the vanes 760 and 770 and to the curved surface of sine wave form formed by the extended curved surface which connects the inner curve a and the outer curve b of the slant compression plate 730, whereby the gap between the slant compression plate 730 and the vanes 760 and 770 is minimized. Therefore, the leakage of the fluid caused by the pressure difference between the suction space of lower pressure and s the compression space of higher pressure can be prevented, and the compression efficiency can be increased.
A compressor of thirteenth embodiment according to the present invention will be described as follows with reference to Figures 51 through 54.
o Figure 51 is a cut perspective view showing principal parts of the compressor of the thirteenth embodiment, Figure 52 is a detailed view showing a stafie of rotating the compressor of Figure 51 as 180°, and Figure 53 is a plane view showing the principal parts of the thirteenth embodiment according to the present invention.
15 Shapes of both sides of vanes 860 and 870 in the compressor are changed so that the fluid is not leaked from the higher pressure side to the lower pressure side between the both sides of the vanes 860 and 870 and inner circumferential surfaces of a rotating shaft 820 and a cylinder 815.
Descriptions for same components as in the twelfth embodiment will 2 o be omitted.
The vanes 860 and 870 of square plate having a certain thickness has one side surface contacted to a hub unit 825 of the rotating shaft 820, and other side surface contacted to inner circumferential surface of the cylinder 815. And the vanes 860 and 870 divide compression spaces V1 p and V2p and suction spaces V1 s and V2s when the fluid is compressed, The both side surfaces of the vanes 860 and 870 are formed as curved surfaces same as the hub unit 825 and as the inner circumferential surface of the cylinder 815 so as to be contacted its surfaces to the hub unit 825 and to the inner circumferential surface of the cylinder 815.
That is, a plate contact curved surface unit 861 having a curvature which is reduced toward outer side as in the twelfth embodiment is formed on the part which is contacted to the slant compression plate 830, and an axial contact curved surface unit 862 of concave shape is formed on the part Zo which is contacted to the hub unit 825 of the rotating shaft 820, In addition a cylinder contact curved surface unit 863 of convex shape is formed on the part which is contacted to the inner circumferential surface of the cylinder 815.
Herein, the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 are formed to have same radiuses of curvature through the entire part of the vanes 860 and 870 in vertical direction.
On the other hand, vane slots 817, in which the vane 860 is inserted, are formed on upper and lower surfaces of a cylinder assembly 810 respectively as shown in Figure 52, and both ends of the vane slots are 2 o formed to have same shapes as those of the both side surfaces of the vane 860.
Figure 54 is a perspective view of the principal parfis showing a modified embodiment of the axial contact curved surface unit of the vane in the compressor of the thirteenth embodiment according to the present invention.
In a vane 860' shown in Figure 54, the curved surface which is contacted to the rotating shaft is formed to have different shapes on intermediate part and both sides parts. The axial contact curved surface unit 862' same as the outer curved surface of the rotating shaft is formed on the center part so as to be contacted its surface to the outer circumferential surface of the rotating shaft, and plane surface units 862' are formed on both sides of the axial contact curved surface unit 862'.
The operation and effect of the compressor in the thirteenth so embodiment according to the present invention will be described as follows.
The first and second vanes 860 and 870 are inserted into the vane slots 817 of the cylinder assembly 810, and moved up and down in the state that the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 are contacted its surfaces to the outer circumferential surface of the rotating shaft 820 and to the inner circumferential surface of the cylinder 815 according to the rotation of the slant compression is rotated. In addition, the vanes 860 and 870 divide the first and second spaces V1 and V2 of the compression space V in the cylinder assembly 810 into the compression spaces V1p and V2p and suction spaces V1s and V2s.
2 o At that time, the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 located on both sides of the first and second vanes 860 and 870 are contacted to the outer circumferenfiial surface of the rotating shaft 820 and to the inner circumferential surface of the cylinder 815, and therefore the leakage of the fluid from the compression spaces V1 p and V2p to the suction spaces V1 s and V2s in the first anu ~C~m m 5~ace5 v ~ anU
V2 is minimized.
As described above, according to the compressor of the thirteenth embodiment, the leakage of the pressure from the higher pressure space to the lower pressure space can by minimized by the contact structure of the vanes 860 and 870, the rotating shaft 820, and the cylinder 815, whereby the compression efficiency of the compressor can be increased.
INDUSTRIAL APPLICABILITY
to As so far described, according to the compressor of the present invention, a slant compression plate of firue circle shape is installed inside the cylinder assembly and compresses the fluid, and therefore an additional balance weight is not needed. Therefore, the vibration and noise which may be generated during the fluid compression processes can be reduced, and s5 at the same time, sufficient driving force can be assured with the motor devices having relatively small capacity.
Also, in the compressor according to the present invention, the volume of the slant compression plate which is installed inside the cylinder assembly is relatively small, and therefore the dead volume in the compression space 2 o can be reduced. In addition, the fluid can be compressed and discharged in both spaces centering around the slant compression plate at the same time, whereby high compression efficiency can be made with a simple structure
Therefore, an object of the present invention is to provide a compressor including a slant compression plate having an upper dead center and a lower dead center inside a compression space, whereby entire structure can be simple, vibration and noise are lowered, and compression efficiency per unit volume is increased.
In order to achieve the above objects, there is provided a compressor comprising: a cylinder assembly having a compression space therein, and a suction flowing passage and a discharge flowing passage are connected to to the compression space; a rotation driving means inserted inside the compression space of the cylinder assembly for transmitting the rotational force; a slant compression plate located inside the compression space of the cylinder assembly for dividing the compression space into two or more spaces, and at the same time, compressing and discharging fluid in the z5 respective spaces through the discharge flowing passage while rotating by being connected to the rotation driving means; and a vane means adhered to both surfaces of the slant compression plate by being inserted inside the compression space of the cylinder assembly so as to perform reciprocating movement, and dividing the respective spaces partitioned by the slant 2 o compression plate into a suction space and a compression space by being located between the suction flowing passage and the discharge flowing passage.
The cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by being coupled to the upper and lower parts of the cylinder and at the same time, supporting the rotation driving means.
A damping recess of a certain depth is formed in the cylinder assembly so as to suck a pressure pulsation generated during fluid compression process inside the compression space.
The suction flowing passage and the discharge flowing passage are formed as two pairs so as to have phase difference of 180°.
A discharge valve is formed on the discharge flowing passage of the cylinder assembly for opening/closing the discharge of the compressed fluid.
to Two suction flowing passages are formed in the cylinder so as to have phase difference of 180°, one of those two is formed on an upper part of the cylinder and the other is formed on a lower part of the cylinder.
A flowing resistance reducing unit which is an emitted part is formed on an entrance unit located on the compression space side of the cylinder z5 assembly so that the flowing resistance generated when the compressed fluid is discharged can be reduced.
A plurality of vane slots are formed on the bearing plates so that the vane means can be inserted and undergoes the reciprocating movement.
A coupling protrusion unit of round shape, which is protruded to inside 20 of the compression space as a certain height and has a outer diameter corresponding to an inner diameter of the cylinder, is formed on the bearing plates.
The slant compression plate is formed to have a plane surface having a plane surface formed as a ring round disk form, and a side surface formed as a sine wave having a upper dead center and a lower dead center adhered to an upper side surface and to a lower side surface of the compression space.
The upper dead center and the lower dead center of the slant compression plate are formed to have a phase difference of 180°, and an angle of a certain horizontal line from the outer circumferential surface to the inner circumferential surface and an outer surface in vertical direction of the rotation driving means is formed to make a right-angle.
The upper dead center and the lower dead center of the slant Zo compression plate may be formed as a curved surface so as to line contact to the upper surface and to the lower surface of the compression space, or may be formed as a plane surface so as fio surface contact to the upper and lower surfaces of the compression space.
The slant compression plate includes a labyrinth seal having afi least s5 one recess band on the outer circumferential surface which is slide contacted to the cylinder assembly so as to prevent a leakage of the fluid from high-pressure side to the low-pressure side by the pressure difference between the respective compression spaces.
The vane means comprises a vane of square shape adhered to the 2 o slant compression plate inside the compression space of the cylinder assembly, and an elastic supporting means supported by the cylinder assembly and providing an elastic force so that the vane is adhered to the slant compression plate.
The vane is disposed on the cylinder assembly to have a phase difference of 180°, and to be adhered to the upper and lower surfaces of the slant compression plate.
The elastic supporting means comprises a spring retainer supported by the cylinder assembly, and a spring supported by the spring retainer for s providing an elastic force to the vane.
A side surface of the vane is formed to be a concave surface so as to surface contact to the outer circumferential surface of the rotating shaft, and the other side surface of the vane is formed to be a convex surface so as to surface contact to the inner circumferential surface of the cylinder assembly.
so The vane comprises a contact curved surface unit of round shape formed on a porfiion to which the slant compression plate is contacted, and the contact curved surface is formed to be enlarged its radius of curvature from the rotational center of the slant compression plate to the outer circumferential surface.
15 According to another embodiment of the present invention, the cylinder assembly has two compression spaces centering around the slant compression plate. In addition, a first suction passage and .a first discharge passage are connected to the first compression space, and a second suction passage and a second discharge passage are connected to the second z o compression space.
The first discharge passage is connected to the second suction passage, whereby the fluid compressed in the first compression space is re-compressed in the second compression space.
According to still another embodiment of the present invention, the s vane means are respectively disposed on same vertical surFace of the cylinder assembly so as to adhere to the upper surface and the lower surface of the slant compression plate.
Two discharge passages are formed in side direction of the cylinder assembly, and some parts of the respective discharge passages are overlapped with the vane means.
The suction passage is formed on side wall of the cylinder assembly so that the fluid is sucked into the both compression spaces in turns accordinc to the rotation of the slant compression plate.
1o A spring penetrating hole is formed on the cylinder assembly so that the elastic supporting means can be passed, and the elastic supporting means is connected to the vanes located on the upper and lower sides of the slant compression plate through the spring penetrating hole, whereby the elastic force can be provided.
BRIEF DESCRIPTION OF THE DRAWINGS
Figure 1 is a cross-sectional view showing a general rotary compressor;
Figure 2 is a cross-sectional view showing a general reciprocating 2 o compressor;
Figure 3 is a cross-sectional view showing a general scroll compressor;
Figure 4 is a longitudinal cross-sectional view showing a compressor according to a first embodiment of the present invention;
Figure 5 is a transverse cross-sectional view showing the compressor according to the first embodiment of the present invention;
Figures 6A, 6B, and 6C are cross-sectional views of line A-A', fine B-B', and line C-C' in Figure 5;
Figure 7 is a cut perspective view showing principal parts of the compressor of the first embodiment according to the present invention;
Figures 8 through 10 are longitudinal cross-sectional view and plane cross-sectional views of principal parts showing operation states of the compressor of the first embodiment according to the present invention;
1o Figure 11 is a longitudinal cross-sectional view showing a compressor of a second embodiment according to the present invention;
Figure 12 is a cut perspective view of principal parts showing the compressor of the second embodiment according to the present invention;
Figures 13A and 13B are longitudinal cross-sectional views showing 25 operation state of the compressor of the second embodiment according to the present invention;
Figure 14 is a view showing status of fluid flowing in the compressor of the second embodiment according to the present invention;
Figure 15 is a longitudinal cross-sectional view showing a compressor 20 of a third embodiment according to the present invention;
Figures 16A, 16B are a transverse cross-sectional view showing the compressor of the third embodiment of the present invention, and a cross-sectional view of line D-D';
Figure 17 is a cut perspective view of principal parts showing the compressor of the third embodiment according to the present invention;
Figures 18A and 18B are cross-sectional views of principal parts showing an another embodiment of a damping recess in the compressor of the third embodiment according to the present invention;
Figure 19 is a transverse cross-sectional view and an enlarged view of principal parts showing a compressor of a fourth embodiment according to the present invention;
Figure 20 is a longitudinal cross-sectional view and an enlarged view showing the compressor of fourth embodiment according to the present invention;
Figures 21 A, 21 B, and 21 C are detailed cross-sectional views of principal parts showing modified embodiments of the damping recess in the compressor of the fourth embodiment according to the present invention;
Figure 22 is a longitudinal cross-sectional view of principal parts s5 showing a compressor of a fifth embodiment according to the present invention;
Figure 23 is a cut perspective view of principal parts showing the compressor of the fifth embodiment according to the present invention;
Figure 24 is a transverse cross-sectional view showing the compressor 2 0 of the fifth embodiment according to the present invention;
Figure 25 is a cut perspective view of principal parts showing a compressor of a sixth embodiment according to the present invention;
Figure 26 is a longitudinal cross-sectional view and detailed view showing the compressor of the sixth embodiment according to the present invention;
Figures 27A and 27B are detailed cross-sectional views of principal parts showing modified embodiments of a flowing resistance reducing unit in the compressor of the sixth embodiment according to the present invention;
Figure 28 is a longitudinal cross-sectional view of principal parts showing a compressor of a seventh embodiment according to the present invention;
Figure 29 is a detailed cross-sectional view of line E-E' in Figure 28;
Figure 30 is a transverse cross-sectional view showing the compressor of the seventh embodiment according to the present invention;
Figure 31 is a cut perspective view of principal parts showing the compressor of the seventh embodiment according to the present invention;
Figure 32 is a cuff perspective view of principal parts showing a compressor of an eighth embodiment according to the present invention;
Figure 33 is a longitudinal cross-sectional view of principal parts showing the compressor of the eighth embodiment according to the present invention;
Figure 34 is a detailed cross-sectional view of line F-F' in Figure 33;
Figure 35 is a longitudinal cross-sectional view of principal parts 2 o showing a compressor of a ninth embodiment according to the present invention;
Figure 36 is a cut perspective view of principal parts showing the compressor of the ninth embodiment according to the present invention;
Figure 37 is a detailed view of principal parts showing the compressor of ninth embodiment according to the present invention;
Figure 38 is a longitudinal cross-sectional view showing a compressor of a tenth embodiment according to the present invention;
Figure 39 is a transverse cross-sectional view showing the compressor of the tenth embodiment according to the present invention;
Figure 40 is a cut perspective view showing the compressor of the tenth embodiment according to the present invention;
Figure 41 is a transverse cross-sectional view of principal parts for describing the compression processes of the compressor of the tenth to embodiment according to the present invention;
Figures 42A, 42B, 42C, and 42D are longitudinal cross-sectional views showing the compression processes of the compressor of the tenth embodiment according to the present invention;
Figure 43 is a longitudinal cross-sectional view showing a compressor 15 of an eleventh embodiment according to the present invention;
Figures 44A and 44B are detailed cross-sectional views of principal parts showing operation state of a vane of the eleventh embodiment according to the present invention;
Figure 45 is a longitudinal cross-sectional view showing a compressor 20 of a twelfth embodiment according to the present invention;
Figure 46 is a cut perspective view showing the compressor of twelfth embodiment according to the present invention;
Figures 47A, 47B, and 47C are a front view, a side view, and an enlarged perspective view of principal parts showing a structure of the vane in the compressor of twelfth embodiment according to the present invention;
Figures 48A and 48B are plane views showing operation state of the compressor of the twelfth embodiment according to the present invention;
Figure 49 is a plane view showing contact status of the vane in accordance with a rotation of the slant compression plate in the compressor of twelfth embodiment according to the present invention;
Figure 50 is a detailed view showing the contact status of the compression sieve unit and the vane in the compressor of the twelfth embodiment according to the present invention;
1 o Figure 51 is a cut perspective view showing a compressor of thirteenth embodiment according to the present invention;
Figure 52 is a detailed view showing a status of rotating the compressor as 180°;
Figure 53 is a plane view showing principal parts of the compressor 15 of the thirteenth embodiment according to the present invention; and Figure 54 is a perspective view showing a modified embodiment a shaft contact surface unit of the vane in the compressor of the thirteenth embodiment according to the present invention.
2 o MODE FOR CARRYING OUT THE PREFERRED EMBODIMENTS
The present invention will now be described with reference to accompanying drawings.
A compressor of a first embodiment according to the present invention will be described with reference to Figures 4 through 12.
Figure 4 is a longitudinal cross-sectional view showing the compressor of the first embodiment according to the present invention, Figure 5 is a transverse cross-sectional view showing the compressor of the first embodiment according to the present invention, Figure 6 is a cross-sectional view of principal parts of lines A-A', B-B', and C-C', and Figure 7 is a cut perspective view showing the compressor of the first embodiment according to the present invention.
The compressor of the first embodiment according to the present invention comprises a motor device unit M for generating a rotation force so inside a casing C, and a compression device unit P for compressing and discharging fluid.
The casing C is formed to have a certain inner volume so as to be sealed, and has at least one or more suction pipe 42 for sucking the fluid formed on one side of the casing and a discharge pipe 43 for discharging the fluid on the other side.
The motor device unit M comprises a stator 44 fixedly coupled to the casing C, and a rotator 45 coupled inside the stator 44 so as to be rotational.
The compression device unit P comprises a cylinder assembly 50 having a compression space V therein and a plurality of suction passages 53 2 o and discharge passages 54 communicating with the compression space V
respectively; a rotating shaft 61 coupled to a rotator 45 of the motor device unit M and penetrating a center portion of the cylinder assembly 50; a slant compression plate 70 coupled to the rotating shaft 61 inside the cylinder assembly 40 and dividing the compression space V of the cylinder assembly 50 into a first space V1, and a second space V2; a first vane 80 and a second vane 80' penetratingly inserted into the cylinder assembly 50, and elastically supported so as to confiact to the both side surfaces of the slant compression plate 70, whereby the vanes undergo a reciprocating movement according to the rotation of the slant compression plate 70 and dividing the compression spaces V1 and V2 as a suction space and a compression space so as to be changeable with each other; and a discharge valve 90 opening/closing the discharge passage 54 of the cylinder assembly and discharging the compressed fluid in the first and the second compression spaces V1 and V2.
1 o Components of the compression device unit P will be described in more detail as follows.
The cylinder assembly 50 comprises a cylinder 55 fixedly installed inside a casing C which has a suction pipe 42 and a discharge pipe 43, and a first bearing plate 56 and a second bearing plate 57 fixed on an upper and a lower sides of the cylinder 55 and forming the compression space V with the cylinder 55.
Herein, the cylinder 55 includes a compression space V therein, and suction passages 53 and 53' communicating with the compression space V
respectively are formed to have a phase difference of 180°.
2 o The suction passages 53 and 53' are formed to have sizes which are able to be opened/closes by the area of side surface thickness of the slant compression plate 70. The suction passage 53 of the first space is formed on upper end part of the cylinder 55, and the suction passage 53' of the second space is formed on lower end part of the cylinder 55.
Shaft holes 56b and 57b, through which the rotating shaft 60 is inserted, are formed on center parts of the first and second bearing plates 56 and 57. Vane slots 56a and 57a having a phase difference of 180° in vertical direction are formed on a side surfaces of the shaft holes 56b and 57b, and the suction passages 53 and 53' and the discharge passages 54 and 54' are disposed on both sides of the vane slots 56a and 57a.
In addition, a first discharge muffler 58 having a large are unit and a small area unit is installed on an upper part of the first bearing plate 56 in order to reduce discharging noise of the fluid discharged from the discharge so passage 54, and a second discharge muffler 59 having a large area unit and a small area unit is installed on a lower part of the second bearing plate 57 in order to reduce discharging noise of the fluid discharged from the discharge passage 54'.
As another embodiment of the cylinder assembly 50, the cylinder 55 15 and the first bearing plate 56 may be formed as a single body, and the second bearing plate 57 may cover the cylinder 55.
Also, as another embodiments of the cylinder assembly 50, the cylinder 55 and the second bearing plate 57 may be formed as a single body, and the first bearing plate 56 may cover the cylinder 55.
2 o In addition, the rotating shaft 60 is press-fitted into the rotator 45, and is penetratingly inserted into the cylinder assembly 50. That is, the rotating shaft 60 is penetratingly inserted into the shaft holes 56b and 57b of the first and second bearing plates 56 and 57, and supported by the first and second bearing plates 56 and 57 so as to rotate relatively.
And, the slant compression plate 70 is formed as ring round disc from plane view, and is formed as a sine wave having an upper dead center R1 and a lower dead center R2 from side view.
That is, on the slant compression plate 70, the upper dead center R1 and the lower dead center R2 are disposed with a phase difference of 180°
therebetween, and is formed as a sine wave when spreading out. And an outer circumferential surface of the slant compression plate 70 is formed as a round when projected from plane view so as to sliding contact to the inner circumferential surface of the cylinder 55.
so In addition, the upper dead center R1 is always slidingly contacted to a bottom surface of the first bearing plate 56, however the lower dead center R2 is disposed to slidingly contact to an upper surface of the second bearing plate 57.
Also, it is desirable that an angle made by a certain horizontal line connected from outer circumferential surface to the inner circumferential surface and by an outer surface of the hub unit 72 in vertical direction is right-angle on the slant compression plate 70.
It is desirable that the thickness of a part making the upper dead center R1 and the lower dead center R2 is formed so as to block the suction 2 o passages 53 and 53' of the cylinder 55 in the slant compression plate 70.
The rotating shaft 60 and the slant compression plate 70 may be formed such that the rotating shaft 60, the hub unit 72, and the slant compression plate 70 are formed as a single body, or these are molded separately and assembled.
Also, the rotating shaft 60 and the hub unit 72, or the hub unit 72 and the slant compression plate 70 may be formed as a single body, and then these may be coupled to another component.
In addition, the vanes 80 and 80' are formed as a square plate so as to have a certain thickness and area, and are inserted into the vane slots 56a and 57a formed on the first and the second bearing plates 56 and 57.
As shown in Figure 7, the vanes 80 and 80' are constructed so as to change the first space V1 and the second space V2 to suction spaces V1 s and V2s, and compression spaces V1 p and V2p respectively, when the slant 1 o compression plate 70 is rotated as contacted to the inner circumferential surface of the cylinder compression space V in the state that the vanes 80 and 80' are contacted to the hub unit 72, to the slant compression plate 70 which are located inside the cylinder compression space V, and to the inner circumferential surface of the cylinder compression space V.
In addition, the vanes 80 and 80' are elastically supported by the elastic supporting means 81 and 81', and the elastic supporting means 81 and 81' are supported by the first and the second bearing plates 56 and 57, respectively.
And, as shown in Figure 6A, the discharge valves 90 and 90' are 2 o installed on the first and the second bearing plates 56 and 57 respectively so as to open/close the discharge passages 54 and 54' through which the fluid compressed in the compression spaces V1 p and V2p of the first and the second spaces V1 and V2 is discharged.
On the other hand, on the bottom surface of the casing C, oil for lubricating and cooling functions is filled on a part where the compression device unit P and the motor device unit M are slidingly contacted. And an oil pump(not shown) for pumping the oil and as oil passage 61 are formed inside the rotating shaft 60.
Operation and effect of the first embodiment according to the present invention will be described as follows.
When an electric current is supplied to the motor device unit M, the rotator 45 and the rotating shaft 60 are rotated. At that time, the first space V1 and the second space V2 of the cylinder 55 are changed into the suction z o spaces V1 s and V2s and compression spaces V1 p and V2p respectively according to the rotation of the slant compression plate 70, and the fluid is sucked into the respective suction passages 53 and 53' of the first and the second spaces V1 and V2 and compressed, and then discharged through the respective discharge passages 54 and 54'.
s5 The processes of suction, compression, and discharging of the fluid according to the rotation of the slant compression plate 70 will be described in more detail with reference to Figures 8 through 10.
Figures 8 through 10 are longitudinal and plane cross-sectional views showing operation states of the compressor in the first embodiment according 2 o to the present invention.
The slant compression plate 70 divides the compression space V of the cylinder 55 into the first space V1 and the second space V2, and the upper dead center R1 and the lower dead center R2 are line contacted to the upper and lower surfaces of the compression space V.
In that state, as shown in Figure 8; when the upper dead center R1 and the lower dead center R2 of the slant compression plate 70 are located between the discharge passages 54 and 54' and the vanes 80 and 80' of the first and the second spaces V1 and V2 respectively, the fluid respectively compressed in the first and the second spaces 54 and 54' are discharged through the discharge passages 54 and 54'.
After that, as shown in Figure 9, when the slant compression plate 70 is rotated to counter-clockwise direction, and the upper and lower dead centers R1 and R2 of the slant compression plate 70 are located between the z o vanes 80 and 80' and the suction passages 53 and 53', then the suction of fluid into the first and the second space V1 and V2 is completed.
In addition, as shown in Figure 10, when the slant compression plate 70 is rotated to counter-clockwise direction, then the upper and lower dead centers R1 and R2 of the slant compression plate 70 are changed into the 15 suction spaces V1 s and V2s and the compression spaces V1 p and V2p in the first and second spaces V1 and V2 by the vane 80 from the position behind the suction passages 53 and 53' to the position before the discharge passages 54 and 54', the fluid in the compression spaces V1 p and V2p is compressed and discharged through the discharge passages 54 and 54', and 2 o at the same time, the fluid is sucked into the suction spaces V1 s and V2s through the suction passages 53 and 53' because of the volume change of the suction spaces V1 s and V2s.
That is, the suction spaces V1 s and V2s suck the fluid as the volume is enlarged, and the compression spaces V1 p and V2p compress the fluid as the volume therein is reduced. Through the processes above, the fluid is sucked, compressed, and discharged in the first and second spaces V1 and V2 at the same time according to the rotation of the slant compression plate 70.
The fluid discharged from the compression space V of the cylinder assembly 50 is discharged out of the casing C through the discharge pipe 43 of the casing C.
The compressor of the first embodiment according to the present invention will be described in views of structure, function, and reliability as s o follows.
The structure of the compressor according to the present invention can be simple because an additional balance weight for balancing the rotation is not used by installing the rotating shaft 60 and the slant compression plate 70.
In addition, a part of the rotating shaft 60 and the slant compression plate 70 which are located inside the compression space V of the cylinder assembly 50 have small volume, and therefore the dead volume is reduced and the compression space is enlarged relatively, whereby the compression efficiency can be increased.
2 o That is, when comparing the compressor according to the present invention to the rotary compressor shown in Figure 1, the dead volume is increased and the compression space is reduced because the rotating shaft 3 and the eccentric unit 3a, and the rolling piston 5 inserted into the eccentric unit 3a are located in the compression space V of the cylinder in case of the rotary compressor, however, the rotating shaft 60 and the slant compression plate 70 are located in the compression space V of the cylinder 55, and the dead volume is reduced and the compression space is increased according to the present invention, whereby the compression efficiency is increased in same cylinder compression space.
Also, according to the present invention, an additional balance weight does not needed, and therefore the torque rotating the rotating shaft 60 to which the slant compression plate 70 is coupled is reduced. Therefore, the electric consumption can be reduced, and sufficient driving force can be Zo ensured by using the motor device unit M having relatively small capacity.
In addition, the rotating shaft 60 and the slant compression plate 70 are balanced with each other, and therefore the vibration noise generated during rotation can be reduced.
That is, eccentric units are installed inside the rotary, reciprocating, and scroll compressors, and therefore the vibration noise is generated.
However, stable rotation can be made, whereby the vibration noise can be reduced.
Also, the slant compression plate 70 is rotated as dividing the cylinder compression space V into the first space V1 and the second space V2, and 2 o accordingly, compression force is pressed to the slant compression plate during the processes of compressing the fluid in the first and the second spaces V1 and V2. At that time, the generated compression force is applied to the first and the second spaces V1 and V2, at the same time, the force of a tangential component of the slanted surface on the slant compression plate 70 is applied as a repulsive power of the torque and the rotating shaft 60 of the motor device unit M. Therefore, the repulsive power applied to the rotating shaft 60 and to the slant compression plate 70 is relatively small, whereby the rotations of the rotating shaft 60 and of the slant compression plate 70 are stable.
In addition, when the rotating shaft 60 and the slant compression plate 70 are rotated, a friction surface where the rotating shaft 60 and the slant compression plate 70 are contacted to each other is relatively small comparing to that of the conventional compressor. Therefore the frictional loss Zo can be reduced, and the amount of oil consumption can be reduced.
A compressor of second embodiment according to the present invention will be described as follows with reference to Figures 11 through 14.
Figure 11 is a longitudinal cross-sectional view showing the Z5 compressor of the second embodiment according to the present invention, Figure 12 is a cut perspective view of principal parts showing the compressor of the second embodiment according to the present invention, Figures 13A
and 13B are longitudinal cross-sectional views showing the operation states of the compressor of the second embodiment according to the present 2 o invention, and Figure 14 is a status view showing the flowing of the fluid in the compressor of the second embodiment according to the present invention.
The compressor of the first embodiment uses the method that the compressor compresses and discharges once in both spaces, however, the compressor uses two-steps compression method by which discharged fluid are cooled and compressed again after one compression is completed.
The compressor of the second embodiment comprises a motor device unit M for generating the rotation force, and a compression device unit P for compressing and discharging the fluid inside the casing C, as in the compressor of the first embodiment.
The compression device unit P comprises a cylinder assembly 110 for forming a compression space V including a cylinder 111, a first bearing plate 113, and a second bearing plate 115, and the cylinder assembly 110 includes a slant compression plate 120 for dividing the compression space V into the to first space V1 and to the second space V2 and rotated by coupling to the rotating shaft 122.
In addition, a first vane 131 and a second vane 132, which are undergone reciprocating movement to opposite axial directions with each other by contacted to the both surfaces of the slant compression plate 120 and divide the respective spaces V1 and V2 into the changeable suction space and the compression space, are installed on the first bearing plate 113 and on the second bearing plate 115.
The cylinder 111 of true round ring form includes a first suction passage 102 on one side connected to,the first space V1 so as to be 2 o connected to fihe suction pipe 101 of the casing C, and a second suction passage 105 is formed as communicated in the second space V2 on the opposite side with a phase difference of 180° with the first suction passage 102.
The first bearing plate 113 includes a firsfi discharge hole 103 for discharging the firstly compressed fluid from the first space V1, and a suction passage 104 is formed on the position having phase difference of 180°
with the first discharge hole 103 for inducing the firstly compressed fluid discharged from the first discharge hole 103 through a second suction passage 105.
A first discharge valve 135 which is opened/closed according to pressure of the fluid in the first space V1 is installed on a front end part of the first discharge hole 103. The discharge valve 135 may be formed as a various shapes, a rectangular discharge valve having a retainer is used in the present Z o invention.
A second discharge hole 106 is formed toward the inner space of the casing C for discharging the fluid secondly compressed in the second space V2 The second bearing plate 115 in the second bearing plate 115, A second discharge valve 136 of same shape as the first discharge valve 135 is 25 installed on a front end part of the second discharge hole 106 so that the second discharge valve 136 can be opened/closed according to the pressure of the fluid in the second space V2.
A first discharge muffler 117 having a large area unit and a small area unit is installed on the upper surface of the first bearing plate 113 so that 2 o discharge noise of the fluid discharged from the first discharge hole 103 is reduced.
It is desirable that the first discharge muffler accepts the first discharge hole 103 and the suction passage 104 of the first bearing plate 113 so as to use these as communication members between the first and the second spaces V1 and V2, and the small area unit is located between the first discharge hole 103 and the suction passage 104.
On the other hand, a discharge hole 107 for discharging the fluid which is secondly compressed in the cylinder assembly 110 to the inside of the s casing C is formed on a second discharge muffler 119 which is located on the opposite position of the first discharge muffler 117.
The operation and effect of the compressor of the second embodiment according to the present invention will be described as follows.
When the electric current is supplied to the motor device unit M and s o the rotating shaft 122 is rotated with the slant compression plate 120, then the fluid is sucked into the first space V1 through the first suction passage 102 of the cylinder 111 and primarily compressed according to the rotation of the slant compression plate 120 as shown in Figure 14. In addition, the primarily compressed fluid pushes the first discharge valve 135 and is discharged into 15 the first discharge muffler 117 through the first discharge hole 103 of the first bearing plate 113 when the pressure of the fluid reaches to a certain degree, and then is sucked into the second space V2 through the suction passage 104 and the second suction passage 105 in the cylinder 111.
The fluid sucked into the second space V2 is secondarily compressed 2 0 by the continuous rotation of the slant compression plate 120. And then, the compressed fluid is discharged while pushing the second discharge valve 136 when the compressed fluid is reached to a certain pressure, and after that, the fluid is discharged into the casing C through the discharge hole 107 of the second discharge muffler 119.
invention and a cross-sectional view showing the line D-D, and Figure 17 is a cut perspective view of the principal parts showing the compressor of the third embodiment according to the present invention.
The compressor of the third embodiment according to the present s invention further comprises damping recesses 158a and 159a are installed in the cylinder assembly 155 so that the noise can be reduced, besides the components of the compressor of the first embodiment.
The compressor of the third embodiment comprises a motor device unit M for generating the rotation force, and a compression device unit P for s o compressing and discharging the fluid in the casing C.
The compression device unit P comprises a cylinder assembly 150 having a compression space; a rotating shaft 160 penetrating the cylinder assembly 150 from the motor device unit M; a slant compression plate 170 of sine wave form for dividing the compression space V in the cylinder z5 assembly 150 into a plurality of spaces; and a plurality of vanes 180A and 180B moving while changing the space in the compression space V into a suction space and a compression space according to the rotation of the slant compression plate 170.
The cylinder assembly 150 comprises a cylinder 150 fixed inside the 2 o casing C; and a first bearing plate 158 and a second bearing plate 159 fixed on an upper and a lower part of the cylinder and forming the compression space V with the cylinder 155.
Especially, the damping recesses 158a and 159a of round recess form having a certain depth are respectively installed on the first bearing plate The fluid discharged into the casing C is compressed twice by the repeated processes that the fluid is discharged to a refrigerating cycle through the discharge pipe 108 of the casing C going through gaps between the respective members.
As described above, the compressor of the second embodiment according to the present invention is suitable for the refrigerating cycle for air conditioning which needs high compression ratio, and load of the motor device unit M, the number of components, and the volume of the compressor can be reduced as the minimum because the fluid can be compressed twice z o in one compression device unit P.
Also, if an upper space is to be the first compression space V1 and a lower space is to be the second compression space V2 in case that the compressor described above is constructed as standing form, then the second compression space V2 has relatively high pressure and supports the s s rotating shaft 122 and the slant compression plate 120. Therefore, the axial load and the pressure of the compressor is reduced, whereby the performance of the compressor can be increased.
A compressor of a third embodiment according to the present invention 2 o will be described as follows with reference to Figures 15 through 18.
Figure 15 is a longitudinal cross-sectional view of principal parts showing the compressor of the third embodiment according to the present invention, Figures 16A and 16B are a transverse cross-sectional view showing the compressor of the third embodiment according to the present and on the second bearing plate 159 so that pressure pulsation of the first space V1 and of the second space V2.
It is desirable that the damping recesses 158a and 159a are formed to be located within 180° from the respective vanes 180A and 180B range toward the rotational direction of the slant compression plate 170, and the damping recesses may be formed on one space between the first and the second spaces V1 and V2.
On the other hand, the compressor of the third embodiment according to the present invention comprises suction passages 153A and 154B and Zo discharge passages 154A and 154B formed in the first and the second spaces V1 and V2 which are divided by the slant compression plate 170, same as in the compressor of the first embodiment according to the present invention.
In addition, vanes 180A and 180B are located respectively between the suction passages 153A and 153B, and the discharge passages 154A and 154B, and the discharge passages 154A and 154B are opened/closed by discharge valves 190A and 190B.
Figures 18A and 18B are cross-sectional views of principal parts showing modified embodiments of the damping recesses in the compressor of the third embodiment according to the present invention.
As shown in Figure 18A, the damping recess 158a' may be formed as an oval, and as shown in Figure 18B, the damping recess 158a" may be formed as two recesses having different inner diameters and stepped inside.
As described above, the damping recess can be modified its shape, size, and number according to the capacity and the condition of the compressor.
The operation and effect of the compressor of the third embodiment according to the present invention will be described as follows.
When the rotating shaft 160 and the slant compression plate 170 are rotated inside the compression space V of the cylinder assembly 150 according to the operation of the motor device unit M, then the first space V1 and the second space V2 are changed into the suction space and the compression space centering around the vanes 180A and 180B. And the fluid 1 o is sucked and compressed through the suction passages 153A and 153B, and the compressed fluid is discharged into the casing C through the discharge passages 154A and 154B.
As described above, in the processes that the fluid is sucked, compressed, and discharged in the first and the second spaces V1 and V2 by the volume change in the first and the second spaces V1 and V2 of the cylinder assembly 150, the pressure pulsation is generated by the pressure change of the fluid. And the pressure pulsation is sucked by the damping recesses 158a and 159a formed in the first and the second spaces V1 and V2.
2 o Therefore, according to the compressor of the third embodiment, the pressure pulsation generated by the pressure change of the fluid is sucked through the damping recesses 158a and 159a, in the processes of sucking, compressing, and discharging the fluid in high temperature and pressure by the rotation of the slant compression plate 170, whereby the noise generated by the pressure pulsation can be reduced.
A compressor of a fourth embodiment according to the present invention will be described as follows with reference to Figures 19 through 21.
s Figure 19 is a longitudinal cross-sectional view and an enlarged view showing the compressor of the fourth embodiment according to the present invention, and Figure 20 is a transverse cross-sectional view and an enlarged view showing the compressor of the fourth embodiment according to the present invention.
1o The compressor of the fourth embodiment according to the present invention comprises damping recesses so as to reduce the pulsation noise as in the compressor of the third embodiment, however the damping recesses are formed on the inner circumferential surface of a cylinder 155' unlike the damping recesses in the compressor of the third embodiment.
15 The compressor of the fourth embodiment comprises a motor device unit M for generating the rotation force and a compression device unit P for compressing and discharging the fluid inside the casing C, and the compression device unit P comprises a cylinder assembly 150', a rotating shaft 160', a slant compression plate 170', and a plurality of vanes 180A' and 20 180B'.
A cylinder 155', a first bearing plate 158', and a second bearing plate 159' are assembled inside the cylinder assembly 150', and therefore a compression space V is formed.
Suction passages 153A' and 153B' respectively communicated with the compression space V are formed to have a phase difFerence of 180°
with each other on the cylinder 155'. In addition, the suction passage 153A' of the first space V1 is formed on an upper part of the cylinder 155', and the suction passage 1538' of the second space V2 is formed on a lower part of the s cylinder 155'.
The suction passages 153A' and 1538' of the first and the second spaces V1 and V2 are formed on positions apart a certain disfiance from the upper and the lower surfaces of the cylinder 155' which are contacted to the first and the second bearing plates 158' and 159'.
to In addition, the slant compression plate 170' is formed to have thicknesses on the upper and lower dead centers can open/close the suction passage 153A' of the first space and the suction passage 1538' of the second space.
Especially, the damping recesses 155A and 1558 are formed between 15 the suction passages 153A' and 1538', and the first and second bearing plate 158' and 159' of the first and second spaces in the cylinder 155' so as to suck the pressure pulsation.
That is, the damping recesses 155A and 1558 are penefiratingly formed from upper or lower sides of the suction passages 153A' and 1538' 2 0 of the first and the second spaces to contacted positions with the first and second bearing plate 158' and 159', and are opened toward the inner circumferential surfaces of the cylinder 155'.
The damping recesses 155A and 1558 as described above are formed as semicircle on the inner circumferential surface of the cylinder 155' as shown in Figure 20 and opened toward the compression space V of the cylinder 155', and the size of the opened part k is same as the diameter of the semicircle.
In addition, it is desirable that the inner diameters of the semicircle of the damping recesses 155A and 155B are formed to be smaller than those of the suction passages 153A' and 153B'.
On the other hand, discharge passages 154A' and 154B' are located on the first and the second bearing plate 158' and 159' so that the fluid compressed inside the first and the second spaces V1 and V2 can be to discharged therethrough.
Figures 21 A, 21 B, and 21 C are detailed cross-sectional views of principal parts showing modified embodiments of the damping recesses in the compressor of the fourth embodiment according to the present invention.
The damping recess 155C shown in Figure 21A is formed by s s overlapping relatively large semicircle and a relatively small circle, and at that time, the small circle is located inward.
And the damping recess 155D shown in Figure 21 B is formed as a circle similar with the damping recess 155A shown in Figure 20, and the size of the opened part toward the compression space is smaller than that of the 2 o damping recess 155A. That is, size of the opened part of the damping recess 155D is smaller than the diameter of the circle.
In addition, the damping recess 155E shown in Figure 21C is formed same as the damping recess 155D in Figure 21 B, however it is installed on a position moved to one side from the center line of the suction passage 153E.
That is, the damping recess 155E is located to have a center point on the position where is not overlapped with the center line of the suction passage 153E.
The operation and efFect of the compressor of the fourth embodiment according to the present invention will be described as follows.
In the compressor of the fourth embodiment according to the present invention, the pressure pulsation caused by the pressure change of the fluid is also generated during the processes of sucking, compressing, and so discharging the fluid in the first and the second spaces V1 and V2 by the volume change of the first and the second spaces V1 and V2 of the cylinder assembly 150', and the.pressure pulsation is sucked by the damping recesses 155A and 155B formed on inner circumferential surface of the cylinder 155' in the first and the second spaces V1 and V2.
That is, the damping recesses 155A and 155B can suck the pressure pulsation of a certain frequency range by changing the inner volume.
The compressor of the fourth embodiment according to the present invention comprises the damping recesses 155a and 155B which suck the pressure pulsation generated by the pressure change of the fluid in the 2 o processes of sucking, compressing, and discharging the fluid while the rotation of the slant compression plate 170', whereby the vibration and noise generated by the pressure pulsation can be reduced and the reliability of the compressor can be increased.
A compressor of a fifth embodiment according to the present invention will be described as follows with reference to Figures 22 through 24.
Figure 22 is a longitudinal cross-sectional view of principal parts showing the compressor of the fifth embodiment according to the present invention, Figure 23 is a cut perspective view showing the compressor of the fifth embodiment according to the present invention, and Figure 24 is a transverse cross-sectional view showing the compressor of the fifth embodiment according to the present invention.
The discharge passages are formed on the first and the second so bearing plate in the compressor of the first embodiment, however discharge passages 205 and 206 are formed penetrating a cylinder 211 in the compressor of the fifth embodiment according to the present invention.
The compressor of the fifth embodiment according to the present invention comprises a casing C, a motor device unit M, and a compression 15 device unit P, and the compression device unit P comprises a cylinder assembly 210, a slant compression plate 220, and a first vane 231 and a second vane 232.
A cylinder 211, a first bearing plate 213, and a second bearing plate 215 are assembled in the cylinder assembly 210, whereby a compression 2 o space V is formed.
A first suction passage 202 is connected to the first space V1 inside the cylinder 211 so as to be connected to the suction pipe 201 in the casing C, and a suction passage 203 connected to another suction pipe(not shown) is communicatively formed in the second space V2 having a phase difference of Z 80° with the first suction passage 202 on the opposite side.
Especially, discharge recess units 211 a and 211 b which are emitted parts having a phase difference of 180° are formed on both sides of the outer circumferential surFace of the cylinder 211, and the discharge passage 205 and 206 are formed on the discharge recess units 211 a and 211 b so that the fluid compressed in the compression space V can be discharged.
In addition, discharge valves 235 and 236 opening/closing the discharge passages 205 and 206 are installed by a bolt inside the discharge recess units 211 a and 211 b, and an engraved recess 211 d having a certain 1 o depth is formed inside the discharge recess units 211 a and 211 b so that the discharge valves can be mounted as shown in Figure 24.
Vanes 231 and 232 are respectively located between the suction passages 202 and 203, and the discharge passages 205 and 206 in the compressor of the fifth embodiment according to the present invention.
The operation of the compressor of the fifth embodiment according to the present invention will be described as follows.
When the rotating shaft 222 and the slant compression plate 220 are rotated inside the compression space V of the cylinder assembly 210 in accordance with the operation of the motor device unit M, then the first space 2 o V1 and fihe second space V2 are respectively changed into the suction space and compression space centering around the respective vane 231 and 232.
Then the fluid is sucked from the suction passages 202 and 203, and compressed. In addition, the compressed fluid is discharged into the casing C through the discharge passage 205 and 206 formed in the cylinder 211 while opening the discharge valves 235 and 236.
A compressor of a sixth embodiment according to the present invention will be described as follows with reference to Figures 25 through 27.
Figure 25 is a cut perspective view of principal parts showing the compressor of the sixth embodiment according to the present invention, and Figure 26 is a transverse cross-sectional view and a detailed view showing the compressor of the sixth embodiment according to the present invention.
Structure of the compressor of the sixth embodiment according to the Zo present invention is similar with that of the compressor of the fifth embodiment, however flowing resistance reducing units 205a and 206a are formed on inlet unit of discharge passages 205' and 206' so that the flowing resistance can be reduced when the compressed fluid is discharged in a cylinder assembly 210'.
15 Descriptions for the same components as those of the fifth embodiment will be omitted.
Two discharge passages 205' and 206' having a phase difference of 180° with each other are formed toward the discharge recess units 211 a' and 219 b' from the compression space V of the cylinder assembly 210' in the 2 o compressor.
The flowing resistance reducing units 205a and 206a which are omitted parts are formed on inlet side the discharge passages 205' and 206' , that is, the compression space V of the cylinder 211 so that the flowing resistance generated when the compressed fluid is discharged.
That is, the discharge passages 205' and 206' are formed as straight lines so as to face the center direction of the compression space V. The flowing resistance units 205a and 206a are formed so that the sizes of the inlet parts of the discharge passages 205' and 206' are larger than those of the outlet parts, and these are slanted so that the size is reduced gradually from the inlet part to the outlet part.
The flowing resistance reducing units 205a and 206a are formed so as to face counterpart direction of rotation of the slant compression plate 220'.
Figures 27A and 27B are detailed cross-sectional views of principal o parts showing modified embodiments of the flowing resistance reducing units in the compressor of the sixth embodiment according to the present invention.
The flowing resistance reducing unit 206c which is narrowed toward the outlet part shown in Figure 27A is formed as a recess having a plurality of steps and having a certain depth.
The flowing resistance reducing unit 206d is formed same as the flowing resistance reducing unit shown in Figure 26, and is slanted so as to be reduced its size toward the outlet part of the discharge passage 206'.
However, the discharge passage 206' is formed as slanted a certain angle 8 against the center direction of the compression space V in the 2 o cylinder 211'.
The operation and effiect of the compressor of the sixth embodiment according to the present invention will be described as follows.
When the slant compression plate 220' is rotated according to operation of the motor device unit M and the upper dead center reaches a position of 210° from the vanes 231' and 232', the discharge valves 235' and 236' are opened and the compressed fluid is discharged into the casing C
through the discharge passages 205' and 206' in which the flowing resistance reducing units 205a and 206a are formed, with reference to Figures 25 and 26.
At that time, a smooth passage without protruded part is formed by the flowing resistance reducing unit when the compressed fluid flows into the discharge passages 205' and 206' inside the compression space V, whereby the flowing resistance of the fluid is reduced.
so Also, the flowing resistance reducing units 205a and 206a funcfiion as resonator for reducing the operation noise of the discharge valves 235' and 236', whereby the noise is reduced and over-compression is prevented.
A compressor of a seventh embodiment according to the present s5 invention will be described as follows with reference to Figures 28 through 31.
Figure 28 is a longitudinal view showing principal parts of the compressor of the seventh embodiment according to the present invention, Figure 29 is a detailed cross-sectional view of line E-E in Figure 28, Figure 30 is a transverse cross-sectional view showing the compressor of the 2 o seventh embodiment according to the present invention, and Figure 31 is a cut perspective view showing the principal parts of the compressor of the seventh embodiment according to the present invention, In the compressor of the seventh embodiment according to the present invention, the adhering structure of the upper dead center R1 and the lower dead center R2 on the slant compression plate 270 is changed so that a leakage of the fluid in the space of high pressure toward the space of lower pressure can be prevented.
The compressor of the seventh embodiment comprises the casing C, the motor device unit M, and the compression device unit P as in the compressor of the first embodiment, and the compression device unit P
comprises a cylinder assembly 250, a rotating shaft 260 and a slant compression plate 270, and a first vane 281 and a second vane 282.
The slant compression plate 270 of ring round disc shape is formed so as a sine wave having the upper dead center R1 and the lower dead center R2 with a phase difference of 180°, and outer circumferential surface of the slant compression plate 270 is formed as a true circle when projected from plane so as to be sildingly contacted to inner circumferential surface of the cylinder 255.
In addition, the upper dead cenfier R1 is always slidingly contacted to a bottom surface of the first bearing plate 256, however the lower dead center R2 is located to be slidingly contacted to an upper surface of the second bearing plate 257 always.
Especially, the slant compression plate 270 is formed as a plane 2 o surface having a certain area so that the upper dead center R1 and the lower dead center R2 are respectively surface contacted to the first and to the second bearing plates 256 and 257.
The slant compression plate 270 may be formed such that the parts on which the upper dead center R1 and the lower dead center R2 are located are cut to be a plane, or may be formed as adding the thickness around the upper dead center R1 and the lower dead center R2 in order to form the plane upper and lower dead centers R1 and R2.
Therefore, the slant compression plate 270 divides the compression space V inside the cylinder assembly 250 into the first and the second spaces V1 and V2 in longitudinal direction, and the plane upper and lower dead centers R1 and R2 divide the respective spaces into the suction space and the discharge space.
The operation and effect of the compressor in the seventh embodiment to according to the present invention will be described as follows.
When the motor device unit M is operated, the rotating shaft 260 and the slant compression plate 270 are rotated inside the cylinder assembly 250.
In addition, the suction, compression, and discharging operations of the fluid are made in the first and the second spaces V1 and V2 according to the z5 rotation of the slant compression plate 270.
Herein, the upper and lower dead centers R1 and R2 are formed as planes, are contacted surfaces to the first and the second bearing plates 256 and 257, and compress the fluid in the first and second spaces V1 and V2, whereby the leakage of the fluid compressed in the compression spaces V1 p 2 o and V2p toward the suction spaces V1 s and V2s can be prevented.
As described above, in the compressor in the seventh embodiment according to the present invention, the contacted area of the slant compression plate 270 and the first and second bearing plates 256 and 257 is increased, and therefore the leakage of the fluid in the compression spaces V1p and V2p to the suction spaces V1s and V2s during compressing the fluid can be reduced, whereby the compression efficiency of the compressor can be increased.
A compressor in an eighth embodiment according to the present invention will be described as follows with reference to Figures 32 through 34.
Figure 32 is a cut perspective view showing principal parts of the compressor in the eighth embodiment according to the present invention, Figure 33 is a longitudinal cross-sectional view showing the compressor of s o the eighth embodiment according to the present invention, and Figure 34 is a detailed cross-sectional view showing the line F-F in Figure 33.
The compressor in the eighth embodiment according to the present invention is constructed such that a labyrinth seal 311 is formed on outer circumferential surface of a slant compression plate 310 and therefore the 15 leakage of compressed fluid between inner circumferential surface of a cylinder 302 and outer circumferential surface of the slant compression plate 310 can be reduced.
That is, the slant compression plate 310 is connected to a rotating shaft 304 in the compression space V of the cylinder 302, and the outer 2 o circumferential surface of the slant compression plate 310 is slidingly contacted to the inner circumferential surface of the cylinder 302. In addition, the slant compression plate 310 divides the compression space V in the cylinder 302 into the first and the second spaces V1 and V2. And a labyrinth seal 311 having one or more recess of band shape is formed on the outer circumferential surface of the slant compression plate 310 so as to prevent the leakage of the compressed fluid.
The shape of cross-section of the labyrinth seal 311 may be formed as a square, as a triangle form(not shown), or as a circular arc(not shown) s when projected from the front side.
Components besides the slant compression plate 310 are similar with those on the first embodiment, and therefore detailed descriptions are omitted.
The operation and effect of the compressor in the eighth embodiment so according to the present invention will be described as follows.
When the slant compression plate 310 is rotated inside the compression space V in the cylinder 302, the first and the second spaces V1 and V2 are divided into the suction spaces V1 s and V2s and the compression spaces V1 p and V2p centering around both vanes 321 and 322, and around 15 the upper and lower dead centers R1 and R2 on the slant compression plate 310.
At that time, the compression space V2p of the second space V2 is located on the lower part of the suction space V1 s of the first space V2, and the suction space V2s of the second space V2 is located on the lower part of 2 o the first space V1 centering around the slant compression plate 310.
That is, one side of the first and the second spaces V1 and V2 becomes the compression space of high pressure, and the other side becomes the suction space of relatively low pressure making the slant compression plate 310 a border.
Therefore, when the fluid pressure in the first space V1 becomes relatively high pressure comparing to that in the second space V2, a part of the fluid in the first space V1 is likely to leak to the second space V2 through the gap between the outer circumferential surface of the slant compression plate 310 and the inner circumferential surface of the cylinder 302.
At that time, the Labyrinth seal 311 is formed on the outer circumferential surface of the slant compression plate 310, and therefore the labyrinth seat reduces the pressure of the fluid which is likely to leak through the gap between the outer circumferential surface of the slant compression Z o plate and the inner circumferential surface of the cylinder 302.
Therefore, the labyrinth seal can prevent the leakage of the fluid from the high pressure space to the lower pressure space.
According to the compressor in the eighth embodiment, the labyrinth seal 311 is formed on the outer circumferential surface of the slant Zs compression plate 310 and minimize the leakage of the fluid from the compression space to the suction space through the gap between the inner circumferential surface of the cylinder 302 and the outer circumferential surface of the slant compression plate 310, whereby the compression efficiency can be increased.
A compressor in a ninth embodiment according to the present invenfiion will be described as follows with reference to Figures 35 through 37.
Figure 35 is a longitudinal cross-sectional view showing principal parts of the compressor in the ninth embodiment according to the present invenfiion, Figure 36 is a cut perspective view showing the principal parts of the compressor in the ninth embodiment according to the present invention, and Figure 37 is a detailed view showing the principal parts of the compressor in the ninth embodiment according to the present invention.
The compressor in the ninth embodiment according to the present invention is constructed such that vanes 481 and 482 can be undergo reciprocating movements smoothly irrespective of around components inside the compression space ~/ of a cylinder assembly 455.
The compressor of the ninth embodiment according to the present Zo invention comprises the casing C, the motor device unit M, and the compression device unit P as in the compressor of the first embodiment, and the compression device unit P comprises a cylinder assembly 450, a rotating shaft 460 and a slant compression plate 470, and a first vane 481 and a second vane 482.
In the cylinder assembly 450, a first bearing plate 430 and a second bearing plate 440 are assembled on an upper side and on a lower side centering around a cylinder 455, and thereby the compression space V is formed therein.
On the first and the second bearing plates 430 and 440, shaft units 2 0 431 and 441 in which the rotating shaft 460 is inserted into center part are formed, and vane slots 433 and 443 having a phase difference of 180° in vertical direction are respectively formed on side surfaces of the shaft units 431 and 441.
Especially, protruded coupling units 435 and 445 of circular shapes, which are protruded inward of the compression space V as a certain height, having outer diameters corresponding to the inner diameter of the cylinder 455 are formed on the first and the second bearing plates 430 and 440.
A hub unit 465 is formed inside the compression space V of the s cylinder assembly 450 so that the slant compression plate 470 can be installed around the rotating shaft 460, and hub coupling recesses 437 and 447 are formed on the first and the second bearing plates 430 and 440 so that upper and lower end parts of the hub unit 465 are inserted into the center part of the protruded coupling units 435 and 445.
z o On the other hand, the slant compression plate 470 is a curved plate of sine wave form on which the upper dead center R1 and the lower dead center R2 are located with a phase difference of 180°. The upper and the lower dead centers R1 and R2 are respectively contacted to the lower and the upper surfaces of the protruded coupling units 435 and 445 and rotated.
15 Also, a plurality of suction passages 456 and 457 are formed on the cylinder 455 through which the fluid is sucked into the compression space V, and the suction passages 456 and 456 are penetratingly formed on positions apart a certain distance from the upper surface and from the bottom surface of the cylinder 455 so as to be located on the lower or the upper side of the 2 o protruded coupling units 435 and 445.
The operation and effect of the compressor in the ninth embodiment according to the present invention will be described as follows.
Three surfaces on frame of the vanes 481 and 482 are contacted respectively to the inner circumferential surface of the cylinder 455, to upper or lower surface of the slant compression plate 470, and to the outer circumferential surface of the hub unit 465 of the rotating unit 460 in the state of being inserted to vane slots 433 and 443, and the vanes are undergone linear reciprocating movement in vertical direction according to the rotation of the slant compression plate 470.
At that time, distance of the reciprocating movement of the vanes 481 and 482 is limited between the bottom surface of the first bearing plate 430 and the upper surface of the protruded coupling unit 445 of the second bearing plate 440.
s o Therefore, front ends of the vanes 481 and 482 are undergone the linear reciprocating movement only inside the compression space V of the cylinder assembly 450, and therefore the front ends of the vanes 481 and 482 are not interrupted by the upper or lower end part of the cylinder 455, and by the upper or lower end part of the hub unit 465, whereby the vanes 481 and 15 482 are able to be undergone smooth reciprocating movement.
Also, the protruded coupling parts 435 and 445 of the first and second bearing plate 430 and 440 are inserted into the compression space V of the cylinder 455, and therefore the positions of the compression space V of the vane slots 433 and 443 and the cylinder 455 are fitted correctly, whereby the 2 o wrong operation of the vanes 430 and 440 caused by the assembling margin can be prevented.
A compressor of a tenth embodiment according to the present invention will be described as follows with reference to Figures 38 through 42.
4s Figure 38 is a longitudinal cross-sectional view showing the compressor in the tenth embodiment, Figure 39 is a transverse cross-sectional view showing principal parts of the compressor in the tenth embodiment according to the present invention, and Figure 40 is a cut ~ perspective view showing the principal parts ofi the compressor in the tenth embodiment according to the present invention.
The compressor of the tenth embodiment according to the present invention is constructed to locate vanes 581 and 582 which are located on both sides of a slant compression plate 570 on same vertical surface.
to The compressor of the tenth embodiment according to the present invention comprises a casing C, a motor device unit M, a compression device unit P, and the compression device unit P comprises a cylinder assembly, a rotafiing shaft 560 and a slant compression plate 570, and a first vane 581 and a second vane 582.
15 A first bearing plate -530 and a second bearing plate 540 are assembled centering around a cylinder 555 on an upper and on a lower side inside the cylinder assembly 550, whereby a compression space V is formed inside.
Herein, a vane slot 531 is formed on the first bearing plate 530 so that 2 o the first vane 581 is inserted and undergone reciprocating movement, and a vane slot 541 is formed on same position of the second bearing plate 540 in vertical direction of the vane slot 531 of the first bearing plate 530.
That is, the vane slot on the first bearing plate 530 and the vane slot 540 on the second bearing plate 540 are formed to be located on same plane as each other.
In addition, a suction passage 556 and discharge passages 557 and 558 are respectively formed on the cylinder 555, the discharge passages 557 and 558 are penetratingly formed from the compression space V of the cylinder assembly 550 to a discharge recess 559 formed on one side of the cylinder 555 as shown in Figure 40. At that time, the first discharge passage 557 and the second discharge passage 558 are formed in a row in vertical direction.
Herein, it is desirable that the discharge passages 557 and 558 are Zo respectively formed on the upper end part and the lower end part of the cylinder 55 so that the compressed fluid in the first and the second spaces V1 and V2, and that the size of the discharge passage is smaller than thickness of the slant compression plate 570.
In addition, discharge valves 591 and 592 for openinglclosing the discharge passages 557 and 558 are installed on the discharge recess 559.
And the suction passage 556 is located on opposite position of the first and the second discharge 557 and 558 centering around the two vanes 581 and 582.
The first and second vanes 581 and 582 are located on same vertical 2o surface centering around the slant compression plate 570, and the suction passage 556 and the discharge passages 557 and 558 are located on both sides of the vanes 581 and 582.
Herein, the first and second vanes 581 and 582 are located to be overlapped with some parts of the first and second discharge passages 557 and 558.
In addition, springs 583 and 584 are respectively located behind the first and second vanes 581 and 582 so that the two vanes 581 and 582 are adhered to the slant compression plate 570, and the springs are supported by spring retainers 585 and 586 which are fixed on the first and second bearing plates 530 and 540.
The operation and effect of the compressor in the tenth embodiment according to the present invention will be described as follows.
When the motor device unit M is operated, the rotating shaft 560 and 1o the slant compression plate 570 inside the cylinder assembly 550 are rotated.
At that time, the slant compression plate 570 is rotated inside the compression space V of the cylinder assembly 550, and accordingly divides and changes the respective spaces of the first and second spaces V1 and V2 into the suction spaces V1 s and V2s and compression spaces V1 p and V2p.
And the fluid is sucked, compressed, and discharged through the suction passage 556 and through the discharge passages 557 and 558.
Herein, the operation of the compressor in the tenth embodiment will be described as follows with reference to Figures 41 and 42.
Figure 41 is a transverse cross-sectional view showing principal parts 2 o for describing the compression processes of the compressor in the tenth embodiment, and Figures 42A, 42B, 42C, and 42D are longitudinal cross-secfiional views showing the compression processes of the compressor in the tenth embodiment according to the present invention.
With reference to Figures 41 and 42, when the upper dead center R1 of the slant compression plate 570 is located on a position P3 between the vanes 581 and 582, then the discharge of the compressed fluid in the first space V1 is completed, and suction and compression of the fluid are processing in the second space V2. At that time, the first vane 581 reaches to highest position, and the second vane 582 also reaches to the highest position.
After that, when the upper dead center R1 of the slant compression plate 570 reaches to a position P4 which is 45° from the first and second vanes 581 and 582, the suction of the fluid is started in the first space V1 and Zo at the same time the compression of the sucked fluid is started. And in the second space V2, the discharge of the compressed fluid becomes completed and at the same time the suction of the fluid is completed.
At that time, the first and second vanes 581 and 582 are located on intermediate position in the compression space V by lowering.
After that, the upper dead center R1 of the slant compression plate 570 reaches to a position P5 of 180° from the first and second vanes 581 and 582 as shown in Figures 41 and 42C, the suction of fluid and the compression of the sucked fluid are processed at the same time in the first space V1, and the discharge of the compressed fluid and the suction of fluid are already 2 o completed in the second space V2.
At that time, the first and second vanes 581 and 582 are located on lowest position in lower part.
After that, the upper dead center R1 of the slant compression plate 570 reaches to a position P6 of 135° from the first and second vanes 581 and 582 as shown in Figures 41 and 42D, the discharge of the compressed fluid and the suction of the fluid are almost completed in the first space V1, and the suction of the fluid is started and the compression of the sucked fluid is processed in the second space V2.
At that time, the first and second vanes 581 and 582 are located on intermediate part of the compression space V by lowering.
As the processes above are repeated, the fluid is sucked, compressed, and discharge into the first and second spaces V1 and V2. And the processes 2 o in the first and second spaces V1 and V2 are not performed at that same time, and performed with a phase difference of 180°.
That is, the discharge of the fluid is made with the phase difference of 180° in the first and second spaces V1 and V2. The discharge fluid from the cylinder assembly as described above is discharged out of the casing C
through the discharge pipe 510 as shown in Figure 38.
According to the compressor of the tenth embodiment, the fluid of high pressure and high temperature compressed respectively inside the first and second spaces V1 and V2 is discharged having phase difference with each other according to the rotation of the rotating shaft 560, and therefore the fluid 2 o is gradually discharged and the pressure pulsation caused by the discharged fluid is reduced.
Also, the processes of the sucking, compressing, and discharging the fluid in the first and second spaces V1 and V2 are processed with different phases with each other, and therefore load torque applied to the motor device unit M is reduced as half of that in case of processing with same phases.
Also, a rotating body having a rotator 561 and the rotating shaft 560 in the motor device unit M is balanced in rotation, and therefore the stable driving is made without the unbalancing of the rotation. In addition, volume which is occupied by the components located in the compression space V of the cylinder assembly 550, that is, the dead volume is reduced, whereby the compression efficiency is increased.
so A compressor of an eleventh embodiment according to the present invention will be described as follows with reference to Figures 43 and 44.
Figure 43 is a longitudinal cross-sectional view showing the compressor in the eleventh embodiment, and Figures 44A and 44B are detailed cross-sectional views of principal parts showing the operation state Of a vane in the eleventh embodiment according to the present invention.
The compressor in the eleventh embodiment according to the present invention comprises two vanes 681 and 682 located on same vertical surface as in the compressor of the tenth embodiment, however a coil spring 685 for supplying an elastic force to the vanes 681 and 682 is constructed as one.
2 o Herein, descriptions for same components as those of the tenth embodiment will be omitted.
In the compressor of the eleventh embodiment according to the present invention, the first and second vanes 681 and 682 are located on the same plane in vane slots 631 and 641 of first and second bearing plates 630 and 640 centering around a slant compression plate 670.
Herein, the first and second vanes 681 and 682 are supplied the elastic force by one elastic connecting member.
The elastic connecting member comprises a first connecting member 683 coupled to the first vane 681, a second connecting member 684 coupled to the second vane 682, and a coil spring 685 connecting the first connecting member 683 and the second connecting member 684.
The first and second connecting members 683 and 684 of rod or plate form having a certain length are coupled behind the first and second vanes s o 681 and 682 respectively.
The coil spring 685 is inserted into the first and second bearing plates 630 and 640 and into spring penetrating holes 633, 643, and 659 penetrating the cylinder 655, and both ends of the coil spring 685 are coupled to the first and second connecting members 684 respectively.
The operation and effect of the compressor in the eleventh embodiment according to the present invention will be described as follows.
The first and second vanes 681 and 682 are moved up and down in accordance with the movement of the slant compression plate 670 in the state that the first and second vanes are respectively contacted to upper and lower 2 o surfaces of the slant compression plate 670 by the elastic force of the coil spring 685.
That is, as shown in Figure 44A, when the upper dead center R1 of the slant compression plate 670 is located on the first and second vanes 681 and 682, the first and second vanes 681 and 682 are adhered to both surfaces of the slant compression plate 670 with a certain force by the elastic force of the coil spring 685, and the first and second vanes 681 and 682 and the coil spring 685 are moved upward.
After that, as shown in Figure 44B, when the slant compression plate 670 is rotated and the lower dead center R2 of the slant compression plate 670 is located on the positions of the first and second vanes 681 and 682, the first and second vanes 681 and 682 are adhered to both surfaces of the slant compression plate 670 by the elastic force of the coil spring 685 with a certain force, and the first and second vanes 681 and 682 and the coil spring 685 are z o moved downward.
As described above, the first and second vanes 681 and 682 and the coil spring 685 are moved up and down together along with the curved surface of the slant compression plate 670 in accordance with the rotation of the slant compression plate 670, and changes the first and second spaces V1 and V2 into the suction space and the compression space.
At that time, the coil spring 685 makes the first and second vanes 681 and 682 be adhered to the slant compression plate 670 with a certain force by set elastic force without distortion of tension or contraction.
Therefore, in the compressor in the eleventh embodiment according 2 o to the present invention, the first and second vanes 681 and 682 are adhered to the slant compression plate 670 with a certain adhering force, and therefore the sealing force of the first and second spaces in which the fluid is sucked and compressed is increased, whereby the compression efficiency is increased. In addition, the structure is simple and the number of the components is small, whereby the production cost can be reduced.
A compressor of a twelfth embodiment according to the present invention will be described as follows with reference to Figures 45 through 50.
Figure 45 is a longitudinal cross-sectional view showing principal parts of the compressor in the twelfth embodiment, Figure 46 is a cut perspective view showing the principal parts of the compressor in the twelfth embodiment, and Figures 47A, 47B, and 47C are a front view, a side view, and an enlarged perspective view showing the structure of a vane in tile compressor of the 2o twelfth embodiment according to the present invention.
The compressor of the twelfth embodiment according to the present invention is constructed so that leakage of fluid from a contacted part of a slant compression plate 730 and vanes 760 and 770 during processes of compressing the fluid can be minimized by improving the structure of the s5 vanes 760 and 770.
Descriptions for same components as those in the first embodiment of the present invention are omitted.
The vanes 760 and 770 included in the compressor of the twelfth embodiment according to the present invention are contacted to the slant 2 o compression plate 730 in the compression space inside a cylinder assembly, and a contacted part T of the vanes 760 and 770 is formed so that a curvature of the contacted part T is gradually enlarged from the rotating center of the slant compression plate 730 toward the outer circumferential surface.
That is, a shown in Figures 47A and 47B, the vanes 760 and 770 are made to have a first curved part f which is contacted to center part of the slant compression plate 730, that is, a rotating shaft 720 side; a second curved part a which is contacted to the outer circumferential surface of the slant compression plate 730, that is, to the inner circumferential surFace of a cylinder 715; and a contact curved part g which is a part connected between the first curved part f and the second curved part e. A radius of curvature of the vanes 760 and 770 is gradually enlarged from the first curved part f to the second curved part e.
Also, the contact curved part g of the vanes 760 and 770 becomes an s o entire curvature by connecting curves in which the radiuses of curvature are gradually increased from center line c of the vanes 760 and 770 in vertical direction, as shown in Figure 47C.
That is, the contact curved part g is formed such that shape of section when cut from a certain position in vertical direction of the vanes 760 and Z5 is a curvature by connecting tangent lines of circles, in which radiuses of curvature are gradually increased from the center line c centering around the center line c.
In addition, a lower end line h which is a center of the contact curved part g is a straight line making a right angle with both side surfaces d and d' 2 0 of the vanes 760 and 770, and a connecting line k which is connecting ends of fihe first curved part f and ends of the second curved part d is formed to be slanted against the lower end line h.
The vanes 760 and 770 as described above are respectively inserted into slots formed on the cylinder assembly 710. Therefore, the contacted part T is contacted to the slant compression plate 730, and the both side surfaces d and d' are respectively contacted to a hub unit of the rotating shaft 720 and to inner circumferential wall of the cylinder 715.
The operation and effect of the compressor in the twelfth embodiment according to the present invention will be described as follows.
Figures 48A and 48B are plane views showing operating states of the compressor in the twelfth embodiment, Figure 49 is a plane view showing contacting state of the vane in accordance with the rotation of the slant compression plate in the compressor of the twelfth embodiment, and figure 50 is a detailed view of the principal parts showing contacting state of the slant compression plate and the vane in the compressor of the twelfth embodiment according to the present invention.
When the upper dead center R1 of the slant compression plate 730 is contacted to the first vane 760 located in the first space V1 and the lower dead center R2 of the slant compression plate 730 is contacted to the second vane 770 located in the second space V2 as shown in Figure 48A, the discharge of compressed fluid and the suction of fluid are completed in the first and second spaces V1 and V2.
At that time, the lower end line h of the vanes 760 and 770 are 2 o accorded respectively with the upper and lower dead centers R1 and R2 of the slant compression plate 730, whereby a sealing line is made.
After that, as shown in Figure 48B, when the upper dead center R1 of the slant compression plate 730 is contacted to the second vane 770 passing through a suction passage 711 of the first space V1 by the rotating shaft 720, and the lower dead center R2 is contacted to the first vane 760 passing through the suction passage 711 of the second space V2, then the compression of fluid sucked in the first and second spaces V1 and V2 respectively is processed, and at the same time, the fluid is sucked.
s Herein, when the first and second vanes 760 and 770 are contacted to the sine wave between the upper and lower dead centers of the slant compression plate 730, the contact line which is contacted to the slant compression plate 730 is changed according the rotation angle of the slant compression plate 730, as shown in Figure 49.
so At that time, the contacted part T, that is, a part including the first and second curved parts f and a and the contact curved part g, on which the vanes 760 and 770 and the slant compression plate 730 are contacted, is formed to correspond to the thickness of the first and second vanes 760 and 770 and to the difference between the curvatures of an upper curve a and a 15 lower curve b, whereby a gap between the slant compression plate 730 and the first and second vanes 760 and 770 can be minimized.
That is, as shown in Figure 50, when the vanes 760 and 770 are located within the range of waveform curved surface of the slant compression plate 730, that is from the front end of the lower dead center R2 to the front 2o end of the upper dead center R1, a contact line, on which the contact curved part g on one side of the vane and the waveform curved surface of the slant compression plate 730 are contacted, is made. In addition, when the vanes 760 and 770 are located within a range of waveform curved surface of the slant compression plate 730, that is from the front end of the upper dead center R1 to the front end of the lower dead center R2, then a contact line, on which the contact curved part g on the other side of the vane and the waveform curved surface of the slant compression plate 730 are contacted, is made.
As described above, the slant compression plate 730 is rotated inside the compression space V of the cylinder assembly 710 by the rotation of the rotating shaft 720, and at the same time, the vanes 760 and 770 contacted to the slant compression plate 730 are moved together, whereby the fluid is sucked, compressed, and discharged continuously.
1o In the first curved part f and the second curved part a of the vanes 760 and 770 located on the sides of outer curve b and of inner curve a of the slant compression plate, and the contact curved surface part g connecting the first and second curved parts f and e, the curvature on the side of the first curved part f is smaller than that of the second curved part e, as in the outer curve 15 b having large curvature than that of the inner curve a of the slant compression plate 730. Therefore, the gap between the slant compression plate 730 and the vanes 760 and 770 for dividing and changing the suction space of lower pressure and the compression space of higher pressure can be minimized.
2 o As described above, as shown in Figure 50, the contacted part of the vanes 760 and 770, which makes the sealing with the slant compression plate 730 by contacting the slant compression plate 730, is formed to be corresponded to the thickness of the vanes 760 and 770 and to the curved surface of sine wave form formed by the extended curved surface which connects the inner curve a and the outer curve b of the slant compression plate 730, whereby the gap between the slant compression plate 730 and the vanes 760 and 770 is minimized. Therefore, the leakage of the fluid caused by the pressure difference between the suction space of lower pressure and s the compression space of higher pressure can be prevented, and the compression efficiency can be increased.
A compressor of thirteenth embodiment according to the present invention will be described as follows with reference to Figures 51 through 54.
o Figure 51 is a cut perspective view showing principal parts of the compressor of the thirteenth embodiment, Figure 52 is a detailed view showing a stafie of rotating the compressor of Figure 51 as 180°, and Figure 53 is a plane view showing the principal parts of the thirteenth embodiment according to the present invention.
15 Shapes of both sides of vanes 860 and 870 in the compressor are changed so that the fluid is not leaked from the higher pressure side to the lower pressure side between the both sides of the vanes 860 and 870 and inner circumferential surfaces of a rotating shaft 820 and a cylinder 815.
Descriptions for same components as in the twelfth embodiment will 2 o be omitted.
The vanes 860 and 870 of square plate having a certain thickness has one side surface contacted to a hub unit 825 of the rotating shaft 820, and other side surface contacted to inner circumferential surface of the cylinder 815. And the vanes 860 and 870 divide compression spaces V1 p and V2p and suction spaces V1 s and V2s when the fluid is compressed, The both side surfaces of the vanes 860 and 870 are formed as curved surfaces same as the hub unit 825 and as the inner circumferential surface of the cylinder 815 so as to be contacted its surfaces to the hub unit 825 and to the inner circumferential surface of the cylinder 815.
That is, a plate contact curved surface unit 861 having a curvature which is reduced toward outer side as in the twelfth embodiment is formed on the part which is contacted to the slant compression plate 830, and an axial contact curved surface unit 862 of concave shape is formed on the part Zo which is contacted to the hub unit 825 of the rotating shaft 820, In addition a cylinder contact curved surface unit 863 of convex shape is formed on the part which is contacted to the inner circumferential surface of the cylinder 815.
Herein, the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 are formed to have same radiuses of curvature through the entire part of the vanes 860 and 870 in vertical direction.
On the other hand, vane slots 817, in which the vane 860 is inserted, are formed on upper and lower surfaces of a cylinder assembly 810 respectively as shown in Figure 52, and both ends of the vane slots are 2 o formed to have same shapes as those of the both side surfaces of the vane 860.
Figure 54 is a perspective view of the principal parfis showing a modified embodiment of the axial contact curved surface unit of the vane in the compressor of the thirteenth embodiment according to the present invention.
In a vane 860' shown in Figure 54, the curved surface which is contacted to the rotating shaft is formed to have different shapes on intermediate part and both sides parts. The axial contact curved surface unit 862' same as the outer curved surface of the rotating shaft is formed on the center part so as to be contacted its surface to the outer circumferential surface of the rotating shaft, and plane surface units 862' are formed on both sides of the axial contact curved surface unit 862'.
The operation and effect of the compressor in the thirteenth so embodiment according to the present invention will be described as follows.
The first and second vanes 860 and 870 are inserted into the vane slots 817 of the cylinder assembly 810, and moved up and down in the state that the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 are contacted its surfaces to the outer circumferential surface of the rotating shaft 820 and to the inner circumferential surface of the cylinder 815 according to the rotation of the slant compression is rotated. In addition, the vanes 860 and 870 divide the first and second spaces V1 and V2 of the compression space V in the cylinder assembly 810 into the compression spaces V1p and V2p and suction spaces V1s and V2s.
2 o At that time, the axial contact curved surface unit 862 and the cylinder contact curved surface unit 863 located on both sides of the first and second vanes 860 and 870 are contacted to the outer circumferenfiial surface of the rotating shaft 820 and to the inner circumferential surface of the cylinder 815, and therefore the leakage of the fluid from the compression spaces V1 p and V2p to the suction spaces V1 s and V2s in the first anu ~C~m m 5~ace5 v ~ anU
V2 is minimized.
As described above, according to the compressor of the thirteenth embodiment, the leakage of the pressure from the higher pressure space to the lower pressure space can by minimized by the contact structure of the vanes 860 and 870, the rotating shaft 820, and the cylinder 815, whereby the compression efficiency of the compressor can be increased.
INDUSTRIAL APPLICABILITY
to As so far described, according to the compressor of the present invention, a slant compression plate of firue circle shape is installed inside the cylinder assembly and compresses the fluid, and therefore an additional balance weight is not needed. Therefore, the vibration and noise which may be generated during the fluid compression processes can be reduced, and s5 at the same time, sufficient driving force can be assured with the motor devices having relatively small capacity.
Also, in the compressor according to the present invention, the volume of the slant compression plate which is installed inside the cylinder assembly is relatively small, and therefore the dead volume in the compression space 2 o can be reduced. In addition, the fluid can be compressed and discharged in both spaces centering around the slant compression plate at the same time, whereby high compression efficiency can be made with a simple structure
Claims (58)
1. A compressor comprising:
a cylinder assembly having a compression space formed therein, and suction passages and discharge passages are connected to the space;
a rotation driving means inserted inside the compression space of the cylinder assembly for transmitting a driving force;
a slant compression plate located inside the compression space of the cylinder assembly for dividing the compression space into two or more spaces, and at the same time, for compressing in the respective spaces and discharging the fluid through the discharge passages while rotating connected to the rotation driving means; and a vane means inserted into the compression space of the cylinder assembly so as to be undergone reciprocating movements and adhered to both surfaces of the slant compression space, for dividing the respective spaces divided by the slant compression plate into suction spaces and compression spaces by being located between the suction spaces and the discharge passages.
a cylinder assembly having a compression space formed therein, and suction passages and discharge passages are connected to the space;
a rotation driving means inserted inside the compression space of the cylinder assembly for transmitting a driving force;
a slant compression plate located inside the compression space of the cylinder assembly for dividing the compression space into two or more spaces, and at the same time, for compressing in the respective spaces and discharging the fluid through the discharge passages while rotating connected to the rotation driving means; and a vane means inserted into the compression space of the cylinder assembly so as to be undergone reciprocating movements and adhered to both surfaces of the slant compression space, for dividing the respective spaces divided by the slant compression plate into suction spaces and compression spaces by being located between the suction spaces and the discharge passages.
2. The compressor of claim 1, wherein the cylinder assembly is fixed inside a sealed casing, and a suction pipe connected with the suction passages and a discharge pipe are installed inside the sealed casing.
3. The compressor of claim 2, wherein the rotation driving means comprises an electric motor installed inside the sealed casing, and a rotating shaft inserted into the compression space of the cylinder assembly from the electric motor for driving the slant compression plate.
4. The compressor of claim 3, wherein oil is filled inside the sealed casing, an oil passage through which the oil flows is formed inside the rotating shaft, and an oil pump for sucking up the oil by the rotation of the rotating shaft is formed on the oil pump.
5. The compressor of claim 1, wherein the cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by coupling to upper and lower parts of the cylinder and supporting the rotation driving means.
6. The compressor of claim 5, wherein two suction passages are formed to have a phase difference of 180° in the cylinder, one is formed on upper end part of the cylinder, and the other is formed on lower end part of the cylinder
7. The compressor of claim 5, wherein the discharge passages through which the fluid compressed in the compression space is discharged are formed on the bearing plates, and a muffler is installed on outer part of the bearing plates so as to reduce discharge noise of the fluid.
8. The compressor of claim 5, wherein a plurality of vane slots are formed on the bearing plates so that the vane means can be inserted and undergone the reciprocating movement.
9. The compressor of claim 5, wherein a protruded coupling unit of circular shape, which is protruded into the compression space at a certain height and has an outer diameter corresponding to an inner diameter of the cylinder, is formed on the bearing plates.
10. The compressor of claim 9, wherein the slant compression plate is formed as a sine wave having an upper dead center and a lower dead center adhered to the upper side surface and to the lower side surface of the compression space, and makes the movement range of the vane means be limited between the protruded coupling unit by rotating with the upper and lower dead centers coupled to the protruded coupling unit.
11. The compressor of claim 9, wherein the rotation driving means includes a hub unit extended toward the circumferential direction on the circumference of the rotation driving means so that the slant compression plate can be installed, and a hub coupling recess is formed on the bearing plates so that a part of the hub unit is inserted into the center part of the protruded coupling unit.
12. The compressor of claim 1, wherein two suction passages and two discharge passages are disposed in the cylinder assembly, phase differences between the two suction passages and between the two discharge passages are all 180°, and the vane means are located respectively between the suction passage and the discharge passage which are adjacent with each other.
13. The compressor of claim 1, wherein two compression spaces are formed centering around the slant compression plate inside the cylinder assembly, the first suction passage and the first discharge passage are connected into the first compression space, and the second suction passage and the second discharge passage are connected into the second compression space.
14. The compressor of claim 13, wherein the cylinder assembly is fixed inside the sealed casing and the suction pipe and the discharge pipe are installed in the sealed casing; and the first and second suction passages are connected to the suction pipe, and the first and second discharge passages are communicated into the sealed casing.
15. The compressor of claim 13, wherein the first discharge passage is connected to the second suction passage, and therefore the fluid compressed in the first compression space is re-compressed in the second compression space.
16. The compressor of claim 15, wherein the cylinder assembly comprises a cylinder having the first and second suction passages, a first and a second bearing plates having the first and second discharge passages coupled to the upper and lower part of the cylinder respectively, and a first and second mufflers respectively installed outside of the first and second bearing plates for reducing the discharge noise of the fluid; and the second suction passage is connected to inside of the first muffler and the second muffler has a discharge hole so that re-compressed fluid can be discharged outside.
17. The compressor of claim 16, wherein the second suction passage is formed penetrating the first bearing plate and the cylinder.
18. The compressor of claim 1, wherein a damping recesse having a certain depth is formed inside the compression space of the cylinder so that pressure pulsation generated during the process of compressing the fluid can be sucked therethrough.
19. The compressor of claim 18, wherein the damping recess is formed to be located within 180° toward the rotation direction of the slant compression plate from the vane means.
20. The compressor of claim 18, wherein the damping recess is formed in all spaces divided by the slant compression plate respectively.
21. The compressor of claim 18, wherein the cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by coupling to the upper and lower parts of the cylinder and at the same time, supporting the rotation driving means; and the damping recesses are respectively formed on the bearing plates.
22. The compressor of claim 18, wherein the damping recess is formed as a circle or a oval shape.
23. The compressor of claim 18, wherein the damping recess is a recess having a plurality of steps of different inner diameters.
24. The compressor of claim 18, wherein the suction passage is formed on a position a certain distance apart from the upper or lower side surface of the compression space in the cylinder assembly, and the damping recess is formed to be opened toward the compression space from the suction passages to the upper or lower side surface of the compression space.
25. The compressor of claim 24, wherein the slant compression plate is formed as a sine wave having an upper dead center and a lower dead center adhered to the upper and lower side surfaces of the compression space, and thickness of the upper and lower dead centers is formed so as to block the suction passages.
26. The compressor of claim 24, wherein the damping recess is formed as a cylinder smaller than the inner diameter of the suction passage.
27. The compressor of claim 24, wherein the cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by coupling to the upper and lower parts of the cylinder, and the damping recess is formed penetrating from the upper or lower part of the suction passage to the bottom or upper surface of the bearing plate.
28. The compressor of claim 1, wherein a discharge valve for opening/closing discharge of the compressed fluid is disposed on the discharge passage of the cylinder assembly.
29. The compressor of claim 1, wherein the cylinder assembly comprises a cylinder, and a plurality of bearing plates forming the compression space by coupling to the upper and lower parts of the cylinder;
and a discharge recess of emitted shape is formed at least on one outer circumferential surface of the cylinder, and the discharge passage is formed penetrating from the compression space to the discharge recess.
and a discharge recess of emitted shape is formed at least on one outer circumferential surface of the cylinder, and the discharge passage is formed penetrating from the compression space to the discharge recess.
30. The compressor of claim 29, wherein a discharge valve for opening/closing the discharge passage is installed on the discharge recess.
31. The compressor of claim 1, wherein a flowing resistance reducing unit which is an emitted part is formed on inlet unit around the compression space of the cylinder so that the flowing resistance generated when the compressed fluid is discharged can be reduced.
32. The compressor of claim 31, wherein the flowing resistance reducing unit is slanted so as to face counterpart direction of the rotating direction of the slant compression plate.
33. The compressor of claim 31, wherein the flowing resistance reducing unit is formed as a recess having a plurality of steps which are narrowed toward the inside of the discharge passage.
34. The compressor of claim 31, wherein a center of the discharge passage is slanted as a certain angle against the rotating center of the slant compression plate.
35. The compressor of claim 1, wherein a plane of the slant compression plate is formed as a ring round disc form, and a side surface of the slant compression plate is formed as a sine wave having an upper dead center and a lower dead center which are adhered to the upper and lower side surfaces of the compression space.
36. The compressor of claim 35, wherein the upper and lower dead centers of the slant compression plate are formed to have a phase difference of 180°.
37. The compressor of claim 35, wherein a certain horizontal line connecting the outer circumferential surface to the inner circumferential surface of the slant compression plate and the outer side surface of the rotation driving means in vertical direction make a right angle.
38. The compressor of claim 35, wherein the suction passages is formed to be contacted to the upper side surface or to the lower side surface of the compression space of the cylinder assembly, and the thickness of the part forming the upper and lower dead centers is formed to have the thickness by which the suction passage of the cylinder assembly can be blocked.
39. The compressor of claim 35, wherein the upper and lower dead centers of the slant compression plate are formed as curved surfaces so as to line contact to the upper and lower side surfaces of the compression space.
40. The compressor of claim 35, wherein the upper and lower dead centers are formed as plane surfaces so as to be contacted its surfaces to the upper and lower side surfaces of the compression space.
41. The compressor of claim 1, wherein a labyrinth seal of one or more recess as a band shape is formed on the outer circumferential surface of the slant compression plate which is slidingly contacted to the cylinder assembly so as to prevent the fluid from being leaked from the high pressure space to the lower pressure space by the pressure difference between the respective spaces which are divided by the slant compression plate.
42. The compressor of claim 1, wherein the vane means comprises vanes of square shape which are adhered to the slant compression plate inside the compression space of the cylinder assembly, and an elastic supporting means which is supported by the cylinder for supplying the elastic force so that the vanes can be adhered to the slant compression plate.
43. The compressor of claim 42, wherein a front end part of the vane is contacted to the slant compression plate and both side parts of the vane are contacted to the inner circumferential surface of the cylinder assembly and to the side surface of the rotation driving means, in the state that the vane is inserted into the upper or lower part of the cylinder so as to be undergone the reciprocating movement.
44. The compressor of claim 42, wherein the vanes are disposed to have a phase difference of 180° on the cylinder assembly, and installed to be adhered to the upper side surface and to the lower side surface of the slant compression plate.
45. The compressor of claim 42, wherein the elastic supporting means comprises a spring retainer supported by the cylinder assembly, and a spring supported by the spring retainer for supplying the elastic force to the vanes.
46. The compressor of claim 42, wherein the vanes are respectively disposed on same vertical surface of the cylinder assembly and adhered to the upper and lower side surfaces of the slant compression plate.
47. The compressor of claim 46, wherein the cylinder assembly comprises a cylinder, and a first and second bearing plates forming the compression space by coupling to the upper and lower parts of the cylinder;
and vane slots are respectively formed on the first and second bearing plates so that the vanes are inserted therein and undergone the reciprocating movement.
and vane slots are respectively formed on the first and second bearing plates so that the vanes are inserted therein and undergone the reciprocating movement.
48. The compressor of claim 46, wherein two discharge passages are formed toward the axial direction of the cylinder assembly, and some parts of the respective passages are overlapped with the side surface of the vanes.
49. The compressor of claim 46, wherein one suction passage is formed on the side wall of the cylinder assembly so that the fluid is sucked into the both compression spaces in turns according to the rotation of the slant compression plate.
50. The compressor of claim 46, wherein a spring penetration hole is formed on the cylinder assembly so that the elastic supporting means can be passed, and the elastic supporting means provides the elastic force by being connected to the vanes located on upper and lower sides of the slant compression plate through the spring penetration hole.
51. The compressor of claim 50, wherein the elastic supporting means comprises a connecting member fixed on the respective vanes, and a coil spring having both ends connected between the connecting member.
52. The compressor of claim 42, wherein the rotation driving means includes a rotating shaft for transmitting the rotation force to inside of the compression space; and one side surface of the vanes are formed as concave curved surfaces so as to be contacted the side surface to the outer circumferential surface of the rotating shaft.
53. The compressor of claim 52, wherein entire one side surface of the vane is formed as a curved surface.
54. The compressor of claim 52, wherein intermediate part of the vane is formed as a curved surface, and both sides of the vane are formed as plane surfaces.
55. The compressor of claim 42, wherein the other side surface of the vane is formed as a convex curved surface so as to be contacted the surface to the inner circumferential surface of the cylinder assembly.
56. The compressor of claim 42, wherein a contact curved surface unit is formed on a part of the vane which is contacted to the slant compression plate.
57. The compressor of claim 56, wherein the contact curved surface unit is formed to have radius of curvature which is gradually increased from the rotating center to the outer circumferential surface of the slant compression plate.
58. The compressor of claim 56, wherein the contact curved surface unit is formed as a curved surface by connecting tangent lines of circles which have radiuses of curvature which are gradually increased from the center line in length direction of the vane to farther positions from the center line.
Applications Claiming Priority (7)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR2000/21955 | 2000-04-25 | ||
| KR1020000021955A KR100324771B1 (en) | 2000-04-25 | 2000-04-25 | Double-stage enclosed compressor |
| KR1020000026760A KR20010105814A (en) | 2000-05-18 | 2000-05-18 | Compressor |
| KR2000/26760 | 2000-05-18 | ||
| KR10-2000-0085808A KR100394239B1 (en) | 2000-12-29 | 2000-12-29 | Vane for compressor |
| KR2000/85808 | 2000-12-29 | ||
| PCT/KR2001/000694 WO2001081765A1 (en) | 2000-04-25 | 2001-04-25 | Compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2407403A1 true CA2407403A1 (en) | 2001-11-01 |
Family
ID=27350222
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002407403A Abandoned CA2407403A1 (en) | 2000-04-25 | 2001-04-25 | Compressor |
Country Status (8)
| Country | Link |
|---|---|
| US (1) | US20030108438A1 (en) |
| EP (1) | EP1276993A4 (en) |
| JP (1) | JP2003532008A (en) |
| CN (1) | CN1430705A (en) |
| AU (1) | AU5679801A (en) |
| BR (1) | BR0110375B1 (en) |
| CA (1) | CA2407403A1 (en) |
| WO (1) | WO2001081765A1 (en) |
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| WO2024044838A1 (en) * | 2022-08-29 | 2024-03-07 | University Of Regina | An annular compression system and a method of operating the same |
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| US8985980B2 (en) | 2013-01-16 | 2015-03-24 | Alberts Generator services inc. | Compressor with rotating cam and sliding end vanes |
| US9695821B2 (en) * | 2013-01-16 | 2017-07-04 | Albert's Generator Services Inc. | Compressor with rotating cam and sliding end vanes |
| CN103967788A (en) * | 2013-02-05 | 2014-08-06 | 珠海格力节能环保制冷技术研究中心有限公司 | Compression assembly, compressor, air conditioner and heat pump water heater |
| JP6065239B2 (en) * | 2013-02-07 | 2017-01-25 | パナソニックＩｐマネジメント株式会社 | Hermetic compressor and refrigeration system |
| CA2886030C (en) | 2015-03-20 | 2021-10-19 | Albert's Generator Services Inc. | Compressor with rotating cam and sliding end vanes |
| US9964109B2 (en) | 2015-12-10 | 2018-05-08 | Albert's Generator Services Inc. | Apparatus for driving fluid having a rotating cam and rocker arm |
| CN105332910B (en) * | 2015-12-15 | 2017-10-31 | 宁昊民 | The reciprocal refrigerant condenser of conjugate hyperbolas |
| CN108087492A (en) * | 2016-11-23 | 2018-05-29 | 上海海立电器有限公司 | A kind of compressor |
| CN113550973B (en) * | 2021-08-26 | 2022-08-16 | 安徽美芝精密制造有限公司 | Crankshaft, compressor and refrigeration equipment |
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| US3994638A (en) * | 1974-08-29 | 1976-11-30 | Frick Company | Oscillating rotary compressor |
| JPS5197006A (en) * | 1975-02-21 | 1976-08-26 | ||
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| US4437823A (en) * | 1979-03-13 | 1984-03-20 | Upravlenie Sanitarno-Tekhnicheskikh Rabot | Rotary machine with an axially moving partition |
| US4385875A (en) * | 1979-07-28 | 1983-05-31 | Tokyo Shibaura Denki Kabushiki Kaisha | Rotary compressor with fluid diode check value for lubricating pump |
| DE3474051D1 (en) * | 1983-05-21 | 1988-10-20 | Sine Pumps | Rotary fluid pump |
| DE3410059A1 (en) * | 1984-03-19 | 1985-09-19 | Werner 6336 Solms Mell | Compressor |
| BR8901185A (en) * | 1989-03-09 | 1990-10-16 | Brasil Compressores Sa | DISCHARGE SYSTEM FOR ROTARY PISTON ROTARY COMPRESSOR |
| JPH06272678A (en) * | 1993-03-23 | 1994-09-27 | Sanyo Electric Co Ltd | Rotary scroll compressor |
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| US5529461A (en) * | 1993-12-27 | 1996-06-25 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Piston type variable displacement compressor |
| JPH07293468A (en) * | 1994-04-28 | 1995-11-07 | Toshiba Corp | Closed type compressor |
| US6189335B1 (en) * | 1998-02-06 | 2001-02-20 | Sanyo Electric Co., Ltd. | Multi-stage compressing refrigeration device and refrigerator using the device |
| JP3011917B2 (en) * | 1998-02-24 | 2000-02-21 | 株式会社ゼクセル | Vane type compressor |
-
2001
- 2001-04-25 CA CA002407403A patent/CA2407403A1/en not_active Abandoned
- 2001-04-25 CN CN01809892.4A patent/CN1430705A/en active Pending
- 2001-04-25 BR BRPI0110375-0A patent/BR0110375B1/en not_active IP Right Cessation
- 2001-04-25 US US10/258,395 patent/US20030108438A1/en not_active Abandoned
- 2001-04-25 WO PCT/KR2001/000694 patent/WO2001081765A1/en not_active Application Discontinuation
- 2001-04-25 EP EP01930254A patent/EP1276993A4/en not_active Withdrawn
- 2001-04-25 AU AU56798/01A patent/AU5679801A/en not_active Abandoned
- 2001-04-25 JP JP2001578822A patent/JP2003532008A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2024044838A1 (en) * | 2022-08-29 | 2024-03-07 | University Of Regina | An annular compression system and a method of operating the same |
Also Published As
| Publication number | Publication date |
|---|---|
| BR0110375B1 (en) | 2010-06-29 |
| US20030108438A1 (en) | 2003-06-12 |
| JP2003532008A (en) | 2003-10-28 |
| WO2001081765A1 (en) | 2001-11-01 |
| BR0110375A (en) | 2004-02-25 |
| AU5679801A (en) | 2001-11-07 |
| EP1276993A1 (en) | 2003-01-22 |
| EP1276993A4 (en) | 2003-10-29 |
| CN1430705A (en) | 2003-07-16 |
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Legal Events
| Date | Code | Title | Description |
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| EEER | Examination request | ||
| FZDE | Discontinued |