EP0515957A1 - Swash plate type compressor - Google Patents
Swash plate type compressor Download PDFInfo
- Publication number
- EP0515957A1 EP0515957A1 EP92108457A EP92108457A EP0515957A1 EP 0515957 A1 EP0515957 A1 EP 0515957A1 EP 92108457 A EP92108457 A EP 92108457A EP 92108457 A EP92108457 A EP 92108457A EP 0515957 A1 EP0515957 A1 EP 0515957A1
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- EP
- European Patent Office
- Prior art keywords
- discharge
- swash plate
- drive shaft
- refrigerant
- pair
- 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.)
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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
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
Definitions
- the present invention relates to swash plate type compressors, and more particularly, it relates to an improved swash plate type compressor for use in vehicles.
- Japanese Unexamined Patent Publication No. 3-92587 discloses a swash plate type compressor which includes a front and rear cylinder blocks.
- a crank case is connected to a refrigerant suction port, and is located at an interface section between the front and rear cylinder blocks.
- Each cylinder block has a distal end which is covered by a corresponding housing section.
- a front valve plate is disposed intermediate the front cylinder block and the front housing section.
- a rear valve plate is disposed intermediate the rear cylinder block and the rear housing section.
- Each housing sections includes a suction chamber and a discharge chamber. The discharge chamber leads to a refrigerant discharge port.
- a drive shaft rotatably enters through an axial opening in the front and rear cylinder blocks.
- a swash plate is fixedly mounted on the drive shaft and is rotatably disposed within the crank case.
- the valve plates include suction ports which connect the suction chambers to a plurality of cylinders, via corresponding suction valves.
- Each valve plate also has a discharge port which connects each discharge chamber with each cylinder via a discharge valve.
- Each cylinder block has a plurality of suction passages which connect the crank case to the front and rear suction chambers, and a discharge passage which interconnects the front and rear discharge chambers.
- the discharge passage is located such that the discharge passage does not interfere with the suction passage and the crank case. Due to design restrictions, such as the limited outer dimensions, the discharge passage has to be positioned close to the suction passage. In this arrangement, however, the refrigerant flows from the refrigerating circuit to the crank case and the suction passage, through the suction ports. The refrigerant absorbs heat from the hot and compressed refrigerant flowing through the discharge passage. The refrigerant is compressed to a higher temperature and is then discharged. As a result, the circulation of the discharged heated refrigerant increases the load on the refrigerating circuit, thus lowering its cooling ability and the overall efficiency of the compressor.
- the swash plate type compressor of the present invention is provided with a plurality of cylinders, and a front and rear cylinder blocks having a crank case connected to a suction port.
- the cylinder blocks are connected to a front and rear housing sections in order to cover the cylinders.
- Each housing section contains a discharge chamber.
- a drive shaft is rotatabley supported by the cylinder blocks. One end of the drive shaft is sealed within the front housing.
- a swash plate is mounted on the drive shaft and is rotatably disposed within the crank case.
- a plurality of two-head pistons engage the swash plate via a pair of shoes.
- the pistons move within their respective cylinders in cooperation with the swash plate.
- the refrigerant is sucked into each cylinder via a suction passage, and is then compressed in each cylinder. Thereafter, it is discharged into the external refrigerating circuit through the front and rear discharge chambers, and the front and rear discharge ports.
- a discharge passage is provided within the drive shaft, and interconnects the front and rear discharge chambers.
- a valve is provided at the end of the discharge passage to control the opening of the discharge port in relation to the pressure difference between the front and rear discharge chambers.
- a primary discharge passage is provided within the drive shaft in order to connect the front and rear discharge chambers.
- a secondary discharge passage is provided to connect the front discharge chamber to the discharge port.
- Fig. 1 illustrates the preferred embodiment of a swash plate type compressor according to the present invention.
- the compressor includes a front and rear cylinder blocks 1 and 2 which are oppositely disposed with respect to each other.
- a crank case 4 is centrally disposed with respect to the cylinder blocks 1 and 2, and leads to a suction port 3.
- the distal end of the front cylinder block 1 and the distal end of the rear cylinder block 2 are covered by a front and rear housing sections 7 and 8.
- a front valve plate 5 and a rear valve plate 6 are disposed intermediate their respective cylinder blocks and housing sections.
- FIG. 2 illustrates a cross sectional view of the front housing section 7, it should be understood that the rear housing section 8 is substantially similarly designed to the front housing section 7.
- the front housing section 7 includes an outer ring shaped front suction chamber 9, which is generally concentrically located around an inner ring shaped front discharge chamber 11.
- the front discharge chamber 11 is in turn concentrically located around a portion of a drive shaft 18.
- the drive shaft 18 rotatably engages an axial opening 1f which extends through the front and rear cylinder blocks 1 and 2, and which is supported by radial bearings 14 and 15 and sealing devices 16 and 17.
- the drive shaft 18 further penetrates through an opening 5c provided in the front valve plate 5, and extends outwardly through the front housing section 7 via a sealing device 19.
- a swash plate 23 is mounted on the drive shaft 18, and rotates within the crank case 4.
- the swash plate 23 is supported by the front and rear cylinder blocks 1 and 2 via thrust bearings 21 and 22 respectively.
- the front and rear cylinder blocks 1 and 2 include a plurality of cylinders such as the cylinders 1a and 2a which are arranged in parallel with the drive shaft 18 at specified intervals therearound.
- Each cylinder 1a or 2a houses a two-head type piston 25.
- Each piston 25 engages the swash plate 23 via a pair of shoes 24.
- the front and rear valve plates 5 and 6 contain suction ports 5a and 6a respectively. These suction ports 5a and 6a connect the front and rear suction chambers 9 and 10 with the cylinders 1a and 2a, via suction valves 30 and 31.
- the front and rear valve plates 5 and 6 also contain discharge ports 5b and 6b respectively. These discharge ports 5b and 6b connect the front and rear discharge chambers 11 and 12 with the cylinders 1a and 2a via discharge valves 30 and 31.
- a plurality of suction passages 32 are provided along the outside circumference of the front and rear cylinder blocks 1 and 2, and connect the crank case 4 with the front and rear suction chambers 9 and 10.
- a bolt 33 penetrates through the suction passage 32, and secures the front and rear housings 7 and 9 together.
- a discharge port 28 is opened to the rear discharge chamber 12.
- the rear discharge chamber 12 is also opened to the axial opening 1f provided in the rear cylinder block 2, via an opening 6c through the rear valve plate 6.
- the drive shaft 18 includes the discharge passage 40 along its axial length.
- the rear end of the discharge passage 40 is opened to the axial opening 1f at the rear end of the drive shaft 18.
- the front end of the discharge passage 40 is open to the front discharge chamber 11 via an opening 40a which includes radial holes or openings that lead to the drive shaft 18.
- the axial opening 1f and the opening or hole 6c substantially form a part of the discharge passage 40.
- the opening 6c contains a valve 41 in the rear discharge chamber 12 to control the opening function of the hole 6c.
- the valve 41 in this embodiment is a reed valve attached to the rear valve plate 6.
- the valve 41 allows the opening of the hole 6c to be freely controlled in relation to the pressure difference between the compressed refrigerant flowing in the front discharge chamber 11 and the rear discharge chamber 12.
- the refrigerant in the external refrigerating circuit flows into the swash plate type compressor via the suction port 3.
- the refrigerant is guided into the crank case 4 and is further guided into the front and rear suction chambers 9 and 10, via their respective suction passages 32.
- the pistons 25 move inside the cylinders 1a and 2a, and are driven by the swash plate 23 and the drive shaft 18.
- the pistons 25 draw the refrigerant into the cylinders 1a and 2a via the suction ports 5a and 6a.
- the refrigerant is then discharged from the cylinders 1a and 2a into the front and rear discharge chambers 11 and 12, via the discharge ports 5b and 6b.
- the compressed refrigerant which was discharged into the front discharge chamber 11 is guided into the discharge passage 40, via the opening 40a.
- the refrigerant mixes with the compressed refrigerant discharged from the rear discharge chamber 12.
- the refrigerant is then discharged into the external refrigerating circuit via the discharge port 28.
- the discharge passage 40 is provided inside the drive shaft 18. Therefore, the refrigerant flowing through the crank case 4 and the suction passage 32 is insulated from the hot discharged refrigerant in the discharge passage 40, which is substantially separated from the crank case 4 and the suction passage 32. In this arrangement, unnecessary heat transfer is avoided.
- the efficiency of the swash plate type compressor of the present invention will now be compared to a conventional swash plate type compressor, based on the number of revolutions and the temperature of the discharged refrigerant.
- the swash plate type compressor of the present invention shows a temperature reduction of about 5°C in the range of 1000 to 3000 rpm. This proves a significant improvement in avoiding heat transfer from the discharge passage 40.
- the inner axial opening in the drive shaft 18 is used as a discharge passage 40. This reduces the weight and size of the compressor main body, and further improves the degree of freedom in designing the main components, including the front and rear cylinder blocks 1 and 2.
- the opening of the hole 6c is controlled by the valve 41 according to the pressure difference between the compressed refrigerant within the front discharge chamber 11 and that within the rear discharge chamber 12.
- the pulsation factors of the compressed refrigerant within the front and rear discharge chambers 11 and 12 are evened out by mutual interference without peak synchronization.
- the amplitude of each pulsation factor is significantly small.
- the frequency referred to herein means the natural frequency of a general type condenser to be connected to the compressor. If the frequency of the condenser were tuned to that of the compressor, resonance may be caused between the condenser and the compressor.
- the swash plate type compressor of the present embodiment however, has substantially no resonance and can suppress noise.
- Fig. 4 illustrates another embodiment of the compressor and includes a modified valve in the drive shaft 18.
- the alternative embodiment includes a new valve design and an opening 6d which is formed slightly larger than that of the preferred embodiment.
- the valve 51 includes a sleeve 52 connected to the rear end of the drive shaft 18, a ball valve 54 built in the sleeve 52 to control the opening of a hole 53, and a spring 55 which forces the ball valve 54 against a valve seat.
- the spring 55 is supported at one end by a stop ring 56.
- the ball valve 54 controls the opening of the hole 53 proportionally to the pressure difference between the compressed refrigerant in the front discharge chamber 11 and that in the rear discharge chamber 12.
- the valve 54 further suppresses the pulsation factors of the compressed refrigerant, in the same way as the compressor of the first embodiment.
- the valve can be replaced by another functionally equivalent type valve, such as a float valve.
- a primary passage 61 similar to the discharge passage of the first embodiment is provided along the shaft axis of the drive shaft 18.
- the rear opening 61a in the primary passage 61 is opened to the rear discharge chamber 12.
- a plurality of through holes or openings 61b are radially provided in the front part of the drive shaft 18.
- Each through hole 61b is outwardly slanted or directed toward the sealing device 19.
- Each through hole 61b also connects the front discharge chamber 11 with the primary passage 61.
- the discharge port 28 is provided in the front housing section 7, such that it is open to the external refrigerating circuit and to the front discharge chamber 11 via a secondary passage 62.
- the refrigerant in the external refrigerating circuit is guided into the crank case 4 via the suction port 3.
- the refrigerant in the crank case 4 is guided into the front and rear suction chambers 9 and 10, via the suction passages 32.
- the refrigerant is compressed inside the cylinders 1a and 2a, and is then discharged into the front and rear discharge chambers 11 and 12.
- the refrigerant within the rear discharge chamber 12 is guided to the primary passage 61 via the opening 61a.
- the refrigerant then mixes with the refrigerant from the front discharge chamber 11 via the hole 61b, and is thereafter discharged into the external refrigerating circuit, via the secondary passage 62 and the discharge port 28.
- the main part of the discharge passage 40 is formed in the drive shaft 18, such that it is separated from the refrigerant suction passage. Therefore, the input refrigerant is sufficiently insulated from the hot and compressed refrigerant in the discharge passage 40.
- the refrigerant flows from the rear discharge chamber 12 to the front discharge chamber 11 through the discharge passage 40.
- the hole 61b is slanted in order to facilitate the flow of the refrigerant. Fluid resistance against the refrigerant in the present design, is smaller than the fluid resistance exerted if the refrigerant there flowing in the opposite direction. Furthermore, the centrifugal force caused by the rotation of the drive shaft 18 acts on the fluid refrigerant through the hole 61b and accelerates the refrigerant flow. As a result, the refrigerant flows quite smoothly.
- the opening 61b which leads to the front discharge chamber 11 can be substantially enclosed with a beltlike reed valve 63, and used as a valve, similarly to the valve in the preferred embodiment.
- a valve 71 can be attached to the through hole 61a which is opened to the rear discharge chamber 12.
- the valve 71 comprises a sleeve 72, a ball valve 73 and a spring 74 etc. like the valve 51.
- the ball valve 73 is positioned at the side of the through hole 61a.
- a swash plate type compressor is provided with a plurality of cylinders and a front and rear cylinder blocks having a crank case connected to a suction port.
- the cylinder blocks are connected to a front and rear housing sections in order to cover the cylinders. Each housing section contains a discharge chamber.
- a drive shaft is rotatable supported by the cylinder blocks. One end of the drive shaft is sealed within the front housing.
- a swash plate is mounted on the drive shaft and is rotatably disposed within the crank case.
- a plurality of two-bead pistons engage the swash plate via a pair of shoes. The pistons move within their respective cylinders in cooperation with the swash plate.
- the refrigerant is sucked into each cylinder via a suction passage, and is then compressed therein.
- the refrigerant is discharged into the external refrigerating circuit through the front and rear discharge chambers, and the front and rear discharge ports.
- a discharge passage is provided within the drive shaft, and interconnects the front and rear discharge chambers.
- a valve is provided at one end of the discharge passage to control the opening of the discharge port in relation to the pressure difference between the front and rear discharge chambers.
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Abstract
Description
- The present invention relates to swash plate type compressors, and more particularly, it relates to an improved swash plate type compressor for use in vehicles.
- Japanese Unexamined Patent Publication No. 3-92587 discloses a swash plate type compressor which includes a front and rear cylinder blocks. A crank case is connected to a refrigerant suction port, and is located at an interface section between the front and rear cylinder blocks. Each cylinder block has a distal end which is covered by a corresponding housing section. A front valve plate is disposed intermediate the front cylinder block and the front housing section. Similarly, a rear valve plate is disposed intermediate the rear cylinder block and the rear housing section. Each housing sections includes a suction chamber and a discharge chamber. The discharge chamber leads to a refrigerant discharge port.
- A drive shaft rotatably enters through an axial opening in the front and rear cylinder blocks. A swash plate is fixedly mounted on the drive shaft and is rotatably disposed within the crank case. The valve plates include suction ports which connect the suction chambers to a plurality of cylinders, via corresponding suction valves. Each valve plate also has a discharge port which connects each discharge chamber with each cylinder via a discharge valve. Each cylinder block has a plurality of suction passages which connect the crank case to the front and rear suction chambers, and a discharge passage which interconnects the front and rear discharge chambers.
- The discharge passage is located such that the discharge passage does not interfere with the suction passage and the crank case. Due to design restrictions, such as the limited outer dimensions, the discharge passage has to be positioned close to the suction passage. In this arrangement, however, the refrigerant flows from the refrigerating circuit to the crank case and the suction passage, through the suction ports. The refrigerant absorbs heat from the hot and compressed refrigerant flowing through the discharge passage. The refrigerant is compressed to a higher temperature and is then discharged. As a result, the circulation of the discharged heated refrigerant increases the load on the refrigerating circuit, thus lowering its cooling ability and the overall efficiency of the compressor.
- It is therefore an object of the present invention to avoid the overheating of the refrigerant.
- It is also an object of the present invention to reduce the size and weight of the compressor.
- In order to achieve the foregoing objects, the swash plate type compressor of the present invention is provided with a plurality of cylinders, and a front and rear cylinder blocks having a crank case connected to a suction port. The cylinder blocks are connected to a front and rear housing sections in order to cover the cylinders. Each housing section contains a discharge chamber.
- A drive shaft is rotatabley supported by the cylinder blocks. One end of the drive shaft is sealed within the front housing. A swash plate is mounted on the drive shaft and is rotatably disposed within the crank case.
- A plurality of two-head pistons engage the swash plate via a pair of shoes. The pistons move within their respective cylinders in cooperation with the swash plate. The refrigerant is sucked into each cylinder via a suction passage, and is then compressed in each cylinder. Thereafter, it is discharged into the external refrigerating circuit through the front and rear discharge chambers, and the front and rear discharge ports.
- A discharge passage is provided within the drive shaft, and interconnects the front and rear discharge chambers. A valve is provided at the end of the discharge passage to control the opening of the discharge port in relation to the pressure difference between the front and rear discharge chambers.
- In another embodiment of the present invention, a primary discharge passage is provided within the drive shaft in order to connect the front and rear discharge chambers. A secondary discharge passage is provided to connect the front discharge chamber to the discharge port.
- The invention, together with objects and advantages thereof, may best be understood by reference to the following description of the presently preferred embodiments together with the accompanying drawings in which:
- Fig. 1 is a sectional view of a swash plate type compressor according to the first embodiment of the present invention;
- Fig. 2 is a cross sectional view of the compressor of Fig. 1, taken along line 2-2;
- Fig. 3 is a graph showing the relationship between the number of revolutions and the temperature of the discharged refrigerant in the compressor of Fig. 1;
- Fig. 4 is a cross sectional view of another embodiment of a swash plate type compressor according to the present invention;
- Fig. 5 is a cross sectional view of yet another embodiment of a swash plate type compressor according to the present invention;
- Fig. 6 is a cross sectional view of the compressor of Fig. 5, taken along line 6-6; and
- Fig. 7 is a cross sectional view of another embodiment of a swash plate type compressor according to the present invention.
- Fig. 1 illustrates the preferred embodiment of a swash plate type compressor according to the present invention. The compressor includes a front and
rear cylinder blocks crank case 4 is centrally disposed with respect to thecylinder blocks suction port 3. The distal end of thefront cylinder block 1 and the distal end of therear cylinder block 2 are covered by a front andrear housing sections front valve plate 5 and arear valve plate 6 are disposed intermediate their respective cylinder blocks and housing sections. - While Fig. 2 illustrates a cross sectional view of the
front housing section 7, it should be understood that therear housing section 8 is substantially similarly designed to thefront housing section 7. Thefront housing section 7 includes an outer ring shapedfront suction chamber 9, which is generally concentrically located around an inner ring shapedfront discharge chamber 11. Thefront discharge chamber 11 is in turn concentrically located around a portion of adrive shaft 18. - The
drive shaft 18 rotatably engages anaxial opening 1f which extends through the front andrear cylinder blocks radial bearings sealing devices drive shaft 18 further penetrates through an opening 5c provided in thefront valve plate 5, and extends outwardly through thefront housing section 7 via asealing device 19. - A
swash plate 23 is mounted on thedrive shaft 18, and rotates within thecrank case 4. Theswash plate 23 is supported by the front andrear cylinder blocks thrust bearings - The front and
rear cylinder blocks cylinders drive shaft 18 at specified intervals therearound. Eachcylinder head type piston 25. Eachpiston 25 engages theswash plate 23 via a pair ofshoes 24. - The front and
rear valve plates suction ports suction ports rear suction chambers cylinders suction valves rear valve plates discharge ports discharge ports rear discharge chambers cylinders discharge valves - A plurality of
suction passages 32 are provided along the outside circumference of the front andrear cylinder blocks crank case 4 with the front andrear suction chambers bolt 33 penetrates through thesuction passage 32, and secures the front andrear housings discharge port 28 is opened to therear discharge chamber 12. Therear discharge chamber 12 is also opened to theaxial opening 1f provided in therear cylinder block 2, via anopening 6c through therear valve plate 6. - One important feature of the swash plate type compressor of the present invention is that the
drive shaft 18 includes thedischarge passage 40 along its axial length. The rear end of thedischarge passage 40 is opened to theaxial opening 1f at the rear end of thedrive shaft 18. The front end of thedischarge passage 40 is open to thefront discharge chamber 11 via anopening 40a which includes radial holes or openings that lead to thedrive shaft 18. Theaxial opening 1f and the opening orhole 6c substantially form a part of thedischarge passage 40. - The opening 6c contains a
valve 41 in therear discharge chamber 12 to control the opening function of thehole 6c. Thevalve 41 in this embodiment is a reed valve attached to therear valve plate 6. Thevalve 41 allows the opening of thehole 6c to be freely controlled in relation to the pressure difference between the compressed refrigerant flowing in thefront discharge chamber 11 and therear discharge chamber 12. - In the above arrangement, the refrigerant in the external refrigerating circuit flows into the swash plate type compressor via the
suction port 3. The refrigerant is guided into the crankcase 4 and is further guided into the front andrear suction chambers respective suction passages 32. Thepistons 25 move inside thecylinders swash plate 23 and thedrive shaft 18. - The
pistons 25 draw the refrigerant into thecylinders suction ports cylinders rear discharge chambers discharge ports - The compressed refrigerant which was discharged into the
front discharge chamber 11 is guided into thedischarge passage 40, via theopening 40a. The refrigerant mixes with the compressed refrigerant discharged from therear discharge chamber 12. The refrigerant is then discharged into the external refrigerating circuit via thedischarge port 28. - As described above, the
discharge passage 40 is provided inside thedrive shaft 18. Therefore, the refrigerant flowing through thecrank case 4 and thesuction passage 32 is insulated from the hot discharged refrigerant in thedischarge passage 40, which is substantially separated from thecrank case 4 and thesuction passage 32. In this arrangement, unnecessary heat transfer is avoided. - The efficiency of the swash plate type compressor of the present invention will now be compared to a conventional swash plate type compressor, based on the number of revolutions and the temperature of the discharged refrigerant. As shown in Fig. 3, the swash plate type compressor of the present invention shows a temperature reduction of about 5°C in the range of 1000 to 3000 rpm. This proves a significant improvement in avoiding heat transfer from the
discharge passage 40. - In the swash plate type compressor of the present invention, the inner axial opening in the
drive shaft 18 is used as adischarge passage 40. This reduces the weight and size of the compressor main body, and further improves the degree of freedom in designing the main components, including the front andrear cylinder blocks - The opening of the
hole 6c is controlled by thevalve 41 according to the pressure difference between the compressed refrigerant within thefront discharge chamber 11 and that within therear discharge chamber 12. In this arrangement, the pulsation factors of the compressed refrigerant within the front andrear discharge chambers - Experiments indicate that pulsation factors at a high frequency of about 300Hz could be suppressed most effectively. The frequency referred to herein means the natural frequency of a general type condenser to be connected to the compressor. If the frequency of the condenser were tuned to that of the compressor, resonance may be caused between the condenser and the compressor. The swash plate type compressor of the present embodiment, however, has substantially no resonance and can suppress noise.
- Fig. 4 illustrates another embodiment of the compressor and includes a modified valve in the
drive shaft 18. In comparison with the design of the compressor in Fig. 1, there is no significant difference between the two designs, with the exception the alternative embodiment includes a new valve design and anopening 6d which is formed slightly larger than that of the preferred embodiment. - In Fig. 4, the
valve 51 includes asleeve 52 connected to the rear end of thedrive shaft 18, aball valve 54 built in thesleeve 52 to control the opening of ahole 53, and aspring 55 which forces theball valve 54 against a valve seat. Thespring 55 is supported at one end by astop ring 56. Theball valve 54 controls the opening of thehole 53 proportionally to the pressure difference between the compressed refrigerant in thefront discharge chamber 11 and that in therear discharge chamber 12. Thevalve 54 further suppresses the pulsation factors of the compressed refrigerant, in the same way as the compressor of the first embodiment. The valve can be replaced by another functionally equivalent type valve, such as a float valve. - Another embodiment of the present invention will now be described with reference to Figs. 5 and 6. This embodiment differs from the first embodiment with respect to the discharge passage. A
primary passage 61 similar to the discharge passage of the first embodiment is provided along the shaft axis of thedrive shaft 18. Therear opening 61a in theprimary passage 61 is opened to therear discharge chamber 12. A plurality of through holes oropenings 61b are radially provided in the front part of thedrive shaft 18. Each throughhole 61b is outwardly slanted or directed toward the sealingdevice 19. Each throughhole 61b also connects thefront discharge chamber 11 with theprimary passage 61. Thedischarge port 28 is provided in thefront housing section 7, such that it is open to the external refrigerating circuit and to thefront discharge chamber 11 via asecondary passage 62. - In this arrangement, the refrigerant in the external refrigerating circuit is guided into the crank
case 4 via thesuction port 3. The refrigerant in thecrank case 4 is guided into the front andrear suction chambers suction passages 32. The refrigerant is compressed inside thecylinders rear discharge chambers rear discharge chamber 12 is guided to theprimary passage 61 via theopening 61a. The refrigerant then mixes with the refrigerant from thefront discharge chamber 11 via thehole 61b, and is thereafter discharged into the external refrigerating circuit, via thesecondary passage 62 and thedischarge port 28. - The main part of the
discharge passage 40 is formed in thedrive shaft 18, such that it is separated from the refrigerant suction passage. Therefore, the input refrigerant is sufficiently insulated from the hot and compressed refrigerant in thedischarge passage 40. - The refrigerant flows from the
rear discharge chamber 12 to thefront discharge chamber 11 through thedischarge passage 40. Thehole 61b is slanted in order to facilitate the flow of the refrigerant. Fluid resistance against the refrigerant in the present design, is smaller than the fluid resistance exerted if the refrigerant there flowing in the opposite direction. Furthermore, the centrifugal force caused by the rotation of thedrive shaft 18 acts on the fluid refrigerant through thehole 61b and accelerates the refrigerant flow. As a result, the refrigerant flows quite smoothly. - Experimentation was conducted to determine the relationship between the number of revolutions of the swash plate type compressor and the temperature of the discharged refrigerant. The results were similar to those of the experimentation of the preferred embodiment. The discharge resistance of the refrigerant within the
discharge passage 40 in the fluid direction was also examined with fixed number of revolutions, such as 1000 rpm. Compared with a refrigerant flowing in the reverse direction, the present embodiment consumes less energy, and therefore offers an improved efficiency of the refrigerant fluid resistance. - The
opening 61b which leads to thefront discharge chamber 11 can be substantially enclosed with abeltlike reed valve 63, and used as a valve, similarly to the valve in the preferred embodiment. - Furthermore, as shown in Fig. 7, a valve 71 can be attached to the through
hole 61a which is opened to therear discharge chamber 12. The valve 71 comprises asleeve 72, aball valve 73 and aspring 74 etc. like thevalve 51. Theball valve 73 is positioned at the side of the throughhole 61a. A swash plate type compressor is provided with a plurality of cylinders and a front and rear cylinder blocks having a crank case connected to a suction port. The cylinder blocks are connected to a front and rear housing sections in order to cover the cylinders. Each housing section contains a discharge chamber. A drive shaft is rotatable supported by the cylinder blocks. One end of the drive shaft is sealed within the front housing. A swash plate is mounted on the drive shaft and is rotatably disposed within the crank case. A plurality of two-bead pistons engage the swash plate via a pair of shoes. The pistons move within their respective cylinders in cooperation with the swash plate. The refrigerant is sucked into each cylinder via a suction passage, and is then compressed therein. The refrigerant is discharged into the external refrigerating circuit through the front and rear discharge chambers, and the front and rear discharge ports. A discharge passage is provided within the drive shaft, and interconnects the front and rear discharge chambers. A valve is provided at one end of the discharge passage to control the opening of the discharge port in relation to the pressure difference between the front and rear discharge chambers.
Claims (5)
- A compressor including a pair of cylinder blocks (1,2) having a plurality of cylinder (1a,2a) and a crank case (4) leading to a suction port (3), a pair of housing sections (7,8) having at least two discharge chambers (11,12), and covering both ends of the pair of cylinder blocks (1,2), a drive shaft (18) being rotatably supported by the pair of cylinder blocks (1,2), a swash plate (23) being mounted on the drive shaft (18) and rotatably housed within the crank case (4), a plurality of pistons (25) engaging the swash plate (23) and moving within the cylinders (1a,2a) in cooperation with the swash plate (23), wherein the refrigerant flows from the suction port (3) into the cylinders (1a,2a) via a suction passage, is compressed within each cylinder (1a,2a), and is discharged into the discharge chambers (11,12) via discharge ports which communicate with the discharge chambers, the compressor being characterized in that:
a discharge passage (40) within the drive shaft (18) and communicating with the discharge chambers (11,12); and
valve means (41,51,71) provided at one end of said discharge passage (40) for communicating with a discharge port (28) provided with the housing sections (7,8), and for controlling the opening of said discharge passage (40) proportionally to the pressure difference between the refrigerant in the discharge chambers (11,12). - The compressor according to claim 1, wherein the pair of housing sections (7,8) includes a front and rear housing sections, wherein the pair of cylinder blocks (1,2) includes a front and rear cylinder blocks, wherein the discharge port (28) is located within said rear housing section (8), and wherein the compressor further includes:
a rear valve plate (6) provided between said rear housing section (8) and the rear cylinder block (2); and
a through hole (6c) provided in the rear valve plate (6) for controlling the opening of said discharge passage (40). - The compressor according to claims 1 or 2, wherein said valve means further includes:
a sleeve (52) in said discharge passage (40), the sleeve (52) having a through hole (53);
a ball valve (54) for controlling the opening of said through hole (53); and
spring means (55) for forcing said ball valve (54) against said through hole (53). - A compressor comprising:
a pair of cylinder blocks (1,2) having a plurality of cylinder (1a,2a) and a crank case (4) leading to a suction port (3), a pair of housing sections (7,8) having at least two discharge chambers (11,12), and covering both ends of the pair of cylinder blocks (1,2), a drive shaft (18) being rotatably supported by the pair of cylinder blocks (1,2), a swash plate (23) being mounted on the drive shaft (18) and rotatably housed within the crank case (4), a plurality of pistons (25) engaging the swash plate (23) and moving within the cylinders (1a,2a) in cooperation with the swash plate (23), wherein the refrigerant flows from the suction port (3) into the cylinders (1a,2a) via a suction passage, and is compressed within each cylinder, and is discharged into the discharge chambers (11,12) via discharge ports which communicate with the discharge chambers (11,12), the compressor being characterized in that:
a primary discharge passage means (61) provided within the drive shaft (18) for causing said discharge chambers (11,12) to fluidly communicate with each other; and
a secondary discharge passage means (62) for causing the front discharge chamber (11) to fluidly communicate with a discharge port (28) provided with the housing sections (7,8). - The compressor according to claim 4, wherein the compressor includes valve means (63, 71) provided at one end of said primary discharge passage means (61) for communicating with the discharge port (28), and for controlling the opening of said primary discharge passage means (61) proportionally to the pressure difference between the refrigerant within the discharge chambers (11,12).
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP3114737A JPH04342881A (en) | 1991-05-20 | 1991-05-20 | Swash plate type compressor |
JP114737/91 | 1991-05-20 | ||
JP3114739A JPH04342882A (en) | 1991-05-20 | 1991-05-20 | Swash plate type compressor |
JP114739/91 | 1991-05-20 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0515957A1 true EP0515957A1 (en) | 1992-12-02 |
EP0515957B1 EP0515957B1 (en) | 1995-12-27 |
Family
ID=26453413
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP92108457A Expired - Lifetime EP0515957B1 (en) | 1991-05-20 | 1992-05-19 | Swash plate type compressor |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0515957B1 (en) |
KR (1) | KR970001757B1 (en) |
DE (1) | DE69207066T2 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5644970A (en) * | 1994-11-22 | 1997-07-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Bearing arrangement in swash plate type compressor with double headed pistons |
CN1040682C (en) * | 1994-07-12 | 1998-11-11 | 株式会社丰田自动织机制作所 | Thrust bearing structure for swash plate compressor |
CN1063526C (en) * | 1994-04-06 | 2001-03-21 | 株式会社丰田自动织机制作所 | Swash plate type compressor |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2479876A (en) * | 1946-04-12 | 1949-08-23 | Steel Products Engineering Co | Pumping apparatus |
FR2443597A1 (en) * | 1978-12-04 | 1980-07-04 | Gen Motors Corp | OSCILLATING PLATE COMPRESSOR |
EP0040477A1 (en) * | 1980-05-20 | 1981-11-25 | General Motors Corporation | Multicylinder swash plate compressor |
-
1992
- 1992-05-19 EP EP92108457A patent/EP0515957B1/en not_active Expired - Lifetime
- 1992-05-19 DE DE69207066T patent/DE69207066T2/en not_active Expired - Fee Related
- 1992-05-20 KR KR1019920008494A patent/KR970001757B1/en not_active IP Right Cessation
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2479876A (en) * | 1946-04-12 | 1949-08-23 | Steel Products Engineering Co | Pumping apparatus |
FR2443597A1 (en) * | 1978-12-04 | 1980-07-04 | Gen Motors Corp | OSCILLATING PLATE COMPRESSOR |
EP0040477A1 (en) * | 1980-05-20 | 1981-11-25 | General Motors Corporation | Multicylinder swash plate compressor |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1063526C (en) * | 1994-04-06 | 2001-03-21 | 株式会社丰田自动织机制作所 | Swash plate type compressor |
CN1040682C (en) * | 1994-07-12 | 1998-11-11 | 株式会社丰田自动织机制作所 | Thrust bearing structure for swash plate compressor |
US5644970A (en) * | 1994-11-22 | 1997-07-08 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Bearing arrangement in swash plate type compressor with double headed pistons |
Also Published As
Publication number | Publication date |
---|---|
KR920021871A (en) | 1992-12-18 |
EP0515957B1 (en) | 1995-12-27 |
DE69207066T2 (en) | 1996-06-20 |
DE69207066D1 (en) | 1996-02-08 |
KR970001757B1 (en) | 1997-02-15 |
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