US20020144591A1 - Swash plate-type variable displacement compressors - Google Patents
Swash plate-type variable displacement compressors Download PDFInfo
- Publication number
- US20020144591A1 US20020144591A1 US10/095,039 US9503902A US2002144591A1 US 20020144591 A1 US20020144591 A1 US 20020144591A1 US 9503902 A US9503902 A US 9503902A US 2002144591 A1 US2002144591 A1 US 2002144591A1
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- Prior art keywords
- swash plate
- compressor
- drive shaft
- mechanical load
- rotor
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- Abandoned
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- 238000006073 displacement reaction Methods 0.000 title claims abstract description 13
- 230000007246 mechanism Effects 0.000 claims abstract description 23
- 230000035515 penetration Effects 0.000 claims abstract description 10
- 239000003507 refrigerant Substances 0.000 description 12
- 238000004378 air conditioning Methods 0.000 description 7
- 230000008901 benefit Effects 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 239000012530 fluid Substances 0.000 description 4
- 230000001154 acute effect Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 238000005094 computer simulation Methods 0.000 description 2
- 230000003247 decreasing effect Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000000593 degrading effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
Images
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
- F04B27/1036—Component parts, details, e.g. sealings, lubrication
- F04B27/1054—Actuating elements
- F04B27/1072—Pivot mechanisms
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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
- F04B27/1054—Actuating elements
Definitions
- the invention relates generally to swash plate-type, variable displacement compressors for use in an air conditioning system of a vehicle. More particularly, the invention relates to swash plate-type, variable displacement compressors having a hinge coupling mechanism positioned between a rotor and a swash plate.
- Compressor (A) for use in an air conditioning system of a vehicle (not shown), such as the known compressor described in Japanese Patent Publication No. 2001-200783, is depicted.
- Compressor (A) includes a front housing 7 , a cylinder block 6 , a rear housing 8 , and a drive shaft 1 .
- Front housing 7 , cylinder block 6 , and rear housing 8 may be fixably attached to each other by a plurality of bolts 15 .
- Drive shaft 1 may pass through the center of front housing 7 and the center of cylinder block 6 .
- Drive shaft 1 also may be rotatably supported by front housing 7 and by cylinder block 6 via a pair of bearings 11 and 12 mounted in front housing 7 and cylinder block 6 , respectively.
- a plurality of cylinder bores 6 a may be formed within cylinder block 6 and also may be positioned equiangularly around an axis of rotation 20 of drive shaft 1 .
- a piston 5 may be slidably positioned within each cylinder bore 6 a, such that pistons 5 reciprocate on axes parallel to axis 20 of drive shaft 1 .
- Compressor (A) also includes a rotor 2 , a crank chamber 30 , and a swash plate 3 .
- rotor 2 is fixed to drive shaft 1 , such that drive shaft 1 and rotor 2 rotate together.
- Crank chamber 30 is formed between front housing 7 and cylinder block 6 , and swash plate 3 may be positioned inside crank chamber 30 .
- Swash plate 3 may be slidably connected to each piston 5 via a pair of shoes 4 positioned between swash plate 3 and each of pistons 5 .
- Swash plate 3 may include a penetration hole 3 c formed therethrough at a center portion of swash plate 3 , and drive shaft 1 may extend through penetration hole 3 c .
- Rotor 2 includes a pair of rotor arms 2 a and an oblong hole 2 b formed through each of rotor arms 2 a
- swash plate 3 further includes a pair of swash plate arms 3 a and a pin 3 b extending from each of swash plate arms 3 a
- a hinge mechanism 9 includes rotor arms 2 a , swash plate arms 3 a , oblong holes 2 b , and pins 3 b , and rotor 2 may be connected to swash plate 3 by hinge mechanism 9 .
- a first of pins 3 b may be inserted into and may slidably engage an inner wall of a first of oblong holes 2 b
- a second of pins 3 b may be inserted into and may slidably engage an inner wall of a second of oblong holes 2 b
- the tilt angle of swash plate 3 may be varied with respect to drive shaft 1 , such that the fluid displacement of compressor (A) also may be varied.
- Compressor (A) also may include an electromagnetic clutch (not shown).
- an electromagnetic clutch When the electromagnetic clutch is activated, a driving force from an external driving source (not shown) is transmitted to drive shaft 1 , such that drive shaft 1 , rotor 2 , and swash plate 3 rotate substantially simultaneously about axis 20 of drive shaft 1 .
- swash plate 3 also moves back and forth in a wobbling motion, such that only movement in a direction parallel to axis 20 of drive shaft 1 is transferred from swash plate 3 to pistons 5 .
- each piston 5 reciprocates within its corresponding cylinder bore 6 a and compresses a fluid, eg., a refrigerant, within a compression chamber 50 formed by a top portion of piston 5 , the walls of cylinder bore 6 a , and a valve plate 40 .
- a fluid eg., a refrigerant
- FIG. 2 a partial, cross-sectional view of compressor (A) taken along a line II-II in a direction (Z) is depicted.
- a plane II includes a first axis (x) and a second axis (y), in which second axis (y) includes axis 20 of drive shaft 1 and first axis (x) is perpendicular to second axis (y).
- Plane II also includes an upper dead center portion (P) of swash plate 3 .
- cylinder bores 6 a comprise a first cylinder bore 6 a 1 , a second cylinder bore 6 a 2 , a third cylinder bore 6 a 3 , a fourth cylinder bore 6 a 4 , a fifth cylinder bore 6 a 5 , and a sixth cylinder bore 6 a 6 .
- pistons 5 reciprocate within corresponding cylinder bores 6 a 1 - 6 a 6 , respectively, each of pistons 5 apply an anti-compressive force on swash plate 3 .
- pistons 5 apply anti-compressive forces (f 1 ), (f 2 ), (f 3 ), (f 4 ), (f 5 ), and (f 6 ) on swash plate 3 at positions (x 1 , y 1 ), (x 2 , y 2 ), (x 3 , y 3 ) (x 4 , y 4 ), (x 5 , y 5 ), and (x 6 , y 6 ), respectively.
- Japanese Patent Publication No. HEI 8-49653 describes an exemplary change in force (f i ) relative to a piston stroke phase in compressor (A).
- the resultant anti-compressive force (F) acts on hinge mechanism 9 and is shown at a representative position (R).
- Resultant force (F) and position (R) may be represented by Cartesian coordinates (X R , Y R ), such that the following formulas are satisfied:
- the mechanical load on compressor (A) depends on a difference between a discharge pressure of the refrigerant and a suction pressure of the refrigerant. Moreover, the discharge pressure of the refrigerant and the suction pressure of the refrigerant depend on a thermal load on the air conditioning system, and the thermal load on the air conditioning system depends on a temperature of the vehicle. As such, the mechanical load on compressor (A) continuously changes. When the mechanical load on compressor (A) changes, the magnitude of resultant force (F) acting on hinge mechanism 9 via swash plate 3 also changes. Specifically, when the mechanical load on compressor (A) decreases, result force (F) also decreases, and position (R) moves towards axis 20 of drive shaft 1 .
- position (R) moves away from axis 20 of drive shaft 1 .
- position (R) at which resultant force (F) acts on swash plate 3 moves from a first portion (t 1 ) of a force line (t) to a second portion (t 2 ) of force line (t).
- Second portion (t 2 ) of force line (t) is located further from axis 20 of drive shaft 1 than first portion (t 1 ) of force line (t), and force line (t) is defined as a set of positions (R) in plane II at which resultant force (F) may be located.
- force line (t) is a substantially straight line and a first end of first portion (t 1 ) of force line (t) intersects axis (y) to form an acute angle ⁇ having a value between about 15° and about 25°.
- angle ⁇ depends on the number of cylinder bores 6 a formed within cylinder block 6 and the properties of the refrigerant used in the compressor.
- a technical advantage of the present invention is that the number of parts may be reduced without decreasing performance of the compressors.
- a rotor may comprise a single rotor arm having an oblong hole formed therethrough
- a swash plate may comprise a single swash plate arm having a pin extending therefrom. Consequently, another technical advantage of the present invention is that the manufacturing cost of each of the compressors may be reduced without decreasing performance of the compressors.
- a swash plate-type, variable displacement compressor comprising a front housing, a cylinder block, a rear housing, and a drive shaft rotatably supported by the front housing and by the cylinder block.
- a plurality of cylinder bores are formed within the cylinder block.
- the compressor also comprises a rotor fixed to the drive shaft, such that the rotor and the drive shaft rotate together, and a plurality of pistons, each of which is slidably positioned within a corresponding cylinder bore.
- the compressor further comprises a swash plate having a penetration hole formed through a center portion of the swash plate, such that the drive shaft extends through the penetration hole.
- the swash plate is connected to each of the pistons by a pair of shoes.
- the compressor also comprises a hinge mechanism which connects the rotor to the swash plate, such that a tilt angle of the swash plate varies with respect to an axis of rotation of the drive shaft.
- the hinge mechanism comprises a single rotor arm having an oblong hole formed therethrough, and a single swash plate arm having a pin portion extending therefrom, such that the pin portion slidably engages an inner wall of the oblong hole.
- a resultant force of the mechanical load is located at a point along a first portion of a force line, and an area of engagement between a surface of the pin portion and the inner wall of the oblong hole comprises the first portion of the force line.
- FIG. 1 is a cross-sectional view of a known, swash plate-type, variable displacement compressor.
- FIG. 2 is a partial, cross-sectional view of the compressor of FIG. 1 taken along a line II-II in a direction (Z).
- FIG. 3 is a cross-sectional view of a swash plate-type, variable displacement compressor according to an embodiment of the present invention.
- FIG. 4 is a partial, cross-sectional view of the compressor of FIG. 3 taken along a line IV-IV in a direction (Z).
- FIGS. 3 and 4 like numerals being used for like corresponding parts in the various drawings.
- Compressor (A′) may comprise a front housing 7 , a cylinder block 6 , a rear housing 8 , and a drive shaft 1 .
- Front housing 7 , cylinder block 6 , and rear housing 8 may be fixably attached by a plurality of bolts 15 .
- Drive shaft 1 may pass through the center of front housing 7 and the center of cylinder block 6 .
- Drive shaft 1 also may be rotatably supported by front housing 7 and by cylinder block 6 via a pair of bearing 11 and 12 mounted in front housing 7 and cylinder block 6 , respectively.
- a plurality of cylinder bores 6 a may be formed within cylinder block 6 and also may be positioned equiangularly around an axis of rotation 20 of drive shaft 1 . Moreover, a piston 5 may be slidably positioned within each cylinder bore 6 a , such that pistons 5 reciprocate along axes parallel to an axis 20 of drive shaft 1 .
- Compressor (A′) also may comprise a rotor 2 , a crank chamber 30 , and a swash plate 3 .
- rotor 2 is fixed to drive shaft 1 , such that drive shaft 1 and rotor 2 rotate together.
- Crank chamber 30 is formed between front housing 7 and cylinder block 6 , and swash plate 3 may be positioned inside crank chamber 30 .
- Swash plate 3 may be slidably connected to each piston 5 via a pair of shoes 4 positioned between swash plate 3 and each of pistons 5 .
- Swash plate 3 may include a penetration hole 3 c formed therethrough at a center portion of swash plate 3 , and drive shaft 1 may extend through penetration hole 3 c .
- Rotor 2 may comprise a single rotor arm 2 a ′ and an oblong hole 2 b ′ formed through rotor arm 2 a ′, and swash plate 3 further may comprise a single swash plate arm 3 a ′ and a pin 3 b ′ extending from swash plate arm 3 a ′.
- a hinge mechanism 9 ′ may comprise rotor arm 2 a ′, swash plate arm 3 a ′, oblong hole 2 b ′, and pin 3 b ′, and rotor 2 may be connected to swash plate 3 by hinge mechanism 9 ′.
- pin 3 b ′ may be inserted into and may slidably engage an inner wall of oblong hole 2 b ′.
- pin 3 b ′ may move within oblong hole 2 b ′, the tilt angle of swash plate 3 may be varied with respect to drive shaft 1 , such that the fluid displacement of compressor (A′) also may be varied.
- Compressor (A′) also may comprise an electromagnetic clutch (not shown).
- an electromagnetic clutch When the electromagnetic clutch is activated, an external driving force from an external driving source (not shown) is transmitted to drive shaft 1 , such that drive shaft 1 , rotor 2 , and swash plate 3 rotate substantially simultaneously about axis 20 of drive shaft 1 .
- swash plate 3 also moves back and forth in a wobbling motion, such that only movement in a direction parallel to axis 20 of drive shaft 1 is transferred from swash plate 3 to pistons 5 .
- each piston 5 reciprocates within its corresponding cylinder bore 6 a and compresses a fluid, eg., a refrigerant, within a compression chamber 50 formed by a top portion of piston 5 , the walls of cylinder bore 6 a , and a valve plate 40 .
- a fluid eg., a refrigerant
- FIG. 4 a partial, cross-sectional view of compressor (A′) taken along a line IV-IV in a direction (Z) is depicted.
- a plane II includes a first axis (x) and a second axis (y), in which second axis (y) includes axis 20 of drive shaft 1 and first axis (x) is perpendicular to axis (y).
- Plane II also includes an upper dead center portion (P) of swash plate 3 .
- cylinder bores 6 a comprise a first cylinder bore 6 a 1 , a second cylinder bore 6 a 2 , a third cylinder bore 6 a 3 , a fourth cylinder bore 6 a 4 , a fifth cylinder bore 6 a 5 , and a sixth cylinder bore 6 a 6 .
- pistons 5 reciprocate within corresponding cylinder bores 6 a 1 - 6 a 6 , respectively, each of pistons 5 apply an anti-compressive force on swash plate 3 .
- pistons 5 apply anti-compressive forces (f 1 ), (f 2 ), (f 3 ), (f 4 ), (f 5 ), and (f 6 ) on swash plate 3 at positions (x 1 , y 1 ), (x 2 , y 2 ), (x 3 , y 3 ) (x 4 , y 4 ), (x 5 , y 5 ), and (x 6 , y 6 ), respectively.
- resultant anti-compressive force (F) acts on hinge mechanism 9 ′ and is shown at a representative position (R).
- Resultant force (F) and position (R) may be represented by Cartesian coordinates (X R , Y R ), such that the following formulas are satisfied:
- the mechanical load on compressor (A′) depends on a difference between a discharge pressure of the refrigerant and a suction pressure of the refrigerant. Moreover, the discharge pressure of the refrigerant and the suction pressure of the refrigerant depend on a thermal load on the air conditioning system, and the thermal load on the air conditioning system depends on a temperature of the vehicle. As such, the mechanical load on compressor (A′) continuously changes. When the mechanical load on compressor (A′) changes, the magnitude of resultant force (F) acting on hinge mechanism 9 ′ via swash plate 3 also changes. Specifically, when the mechanical load on compressor (A′) decreases, resultant force (F) also decreases, and position (R) moves towards axis 20 of drive shaft 1 .
- Second portion (t 2 ) of force line (t) is located further from axis 20 of drive shaft 1 than first portion (t 1 ) of force line (t), and force line (t) is defined as a set of positions (R) in plane II at which resultant force (F) may be located.
- force line (t) is a substantially straight line and a first end of first portion (t 1 ) of force line (t) intersects axis (y) to form an acute angle ⁇ having a value between about 15° and about 25°. Nevertheless, it will be understood by those of ordinary skill in the art that the value of angle ⁇ depends on the number of cylinder bores 6 a formed within cylinder block 6 and the properties of the refrigerant used in the compressor.
- a region (S) is defined as an area of engagement between a surface of pin 3 b ′ and the inner wall of oblong hole 2 b ′ in plane II.
- Hinge mechanism 9 ′ may support a greater resultant force (F) when position (R) of resultant force (F) is inside region (S) than when position (R) is outside region (S).
- a size of hinge mechanism 9 ′ may be selected, such that region (S) substantially or entirely includes portion (t 2 ) of force line (t).
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- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
Abstract
A swash plate-type, variable displacement compressor includes a front housing, a cylinder block, a rear housing, and a drive shaft rotatably supported by the front housing and by the cylinder block. The compressor also includes a rotor fixed to the drive shaft, such that the rotor and the drive shaft rotate together, and a plurality of pistons, each of which is slidably positioned within a corresponding cylinder bore. The compressor further includes a swash plate having a penetration hole formed through a center portion of the swash plate. Moreover, the drive shaft extends through the penetration hole and the swash plate is connected to the pistons via a pair of shoes. The compressor also includes a hinge mechanism which connects the rotor to the swash plate. The hinge mechanism includes a single rotor arm having an oblong hole formed therethrough, and a single swash plate arm having a pin portion extending therefrom, such that the pin portion slidably engages an inner wall of the oblong hole. When a mechanical load of the compressor is greater than a predetermined mechanical load, a resultant force of the mechanical load is located at a point along a first portion of a force line, and an area of engagement between a surface of the pin portion and the inner wall of the oblong hole includes the first portion of the force line.
Description
- 1. Field of the Invention
- The invention relates generally to swash plate-type, variable displacement compressors for use in an air conditioning system of a vehicle. More particularly, the invention relates to swash plate-type, variable displacement compressors having a hinge coupling mechanism positioned between a rotor and a swash plate.
- 2. Description of Related Art
- Referring to FIG. 1, a known, swash plate-type, variable displacement compressor (A) for use in an air conditioning system of a vehicle (not shown), such as the known compressor described in Japanese Patent Publication No. 2001-200783, is depicted. Compressor (A) includes a
front housing 7, acylinder block 6, arear housing 8, and adrive shaft 1.Front housing 7,cylinder block 6, andrear housing 8 may be fixably attached to each other by a plurality ofbolts 15.Drive shaft 1 may pass through the center offront housing 7 and the center ofcylinder block 6.Drive shaft 1 also may be rotatably supported byfront housing 7 and bycylinder block 6 via a pair ofbearings front housing 7 andcylinder block 6, respectively. A plurality ofcylinder bores 6a may be formed withincylinder block 6 and also may be positioned equiangularly around an axis ofrotation 20 ofdrive shaft 1. Moreover, apiston 5 may be slidably positioned within each cylinder bore 6 a, such thatpistons 5 reciprocate on axes parallel toaxis 20 ofdrive shaft 1. - Compressor (A) also includes a
rotor 2, acrank chamber 30, and aswash plate 3. Specifically,rotor 2 is fixed to driveshaft 1, such that driveshaft 1 androtor 2 rotate together.Crank chamber 30 is formed betweenfront housing 7 andcylinder block 6, andswash plate 3 may be positioned insidecrank chamber 30. Swashplate 3 may be slidably connected to eachpiston 5 via a pair ofshoes 4 positioned betweenswash plate 3 and each ofpistons 5. Swashplate 3 may include apenetration hole 3 c formed therethrough at a center portion ofswash plate 3, and driveshaft 1 may extend throughpenetration hole 3 c.Rotor 2 includes a pair of rotor arms 2 a and anoblong hole 2 b formed through each of rotor arms 2 a, andswash plate 3 further includes a pair of swash plate arms 3 a and apin 3 b extending from each of swash plate arms 3 a. Ahinge mechanism 9 includes rotor arms 2 a, swash plate arms 3 a,oblong holes 2 b, andpins 3 b, androtor 2 may be connected toswash plate 3 byhinge mechanism 9. Specifically, a first ofpins 3 b may be inserted into and may slidably engage an inner wall of a first ofoblong holes 2 b, and a second ofpins 3 b may be inserted into and may slidably engage an inner wall of a second ofoblong holes 2 b. Moreover, because each ofpins 3 b may move within their correspondingoblong hole 2 b, the tilt angle ofswash plate 3 may be varied with respect to driveshaft 1, such that the fluid displacement of compressor (A) also may be varied. - Compressor (A) also may include an electromagnetic clutch (not shown). When the electromagnetic clutch is activated, a driving force from an external driving source (not shown) is transmitted to drive
shaft 1, such that driveshaft 1,rotor 2, andswash plate 3 rotate substantially simultaneously aboutaxis 20 ofdrive shaft 1. Moreover,swash plate 3 also moves back and forth in a wobbling motion, such that only movement in a direction parallel toaxis 20 ofdrive shaft 1 is transferred fromswash plate 3 topistons 5. Consequently, eachpiston 5 reciprocates within its corresponding cylinder bore 6 a and compresses a fluid, eg., a refrigerant, within acompression chamber 50 formed by a top portion ofpiston 5, the walls of cylinder bore 6 a, and avalve plate 40. - Referring to FIG. 2, a partial, cross-sectional view of compressor (A) taken along a line II-II in a direction (Z) is depicted. A plane II includes a first axis (x) and a second axis (y), in which second axis (y) includes
axis 20 ofdrive shaft 1 and first axis (x) is perpendicular to second axis (y). Plane II also includes an upper dead center portion (P) ofswash plate 3. Moreover, in compressor (A),cylinder bores 6 a comprise a first cylinder bore 6 a 1, a second cylinder bore 6 a 2, a third cylinder bore 6 a 3, a fourth cylinder bore 6 a 4, a fifth cylinder bore 6 a 5, and a sixth cylinder bore 6 a 6. Whenpistons 5 reciprocate withincorresponding cylinder bores 6 a 1-6 a 6, respectively, each ofpistons 5 apply an anti-compressive force onswash plate 3. Specifically,pistons 5 apply anti-compressive forces (f1), (f2), (f3), (f4), (f5), and (f6) onswash plate 3 at positions (x1, y1), (x2, y2), (x3, y3) (x4, y4), (x5, y5), and (x6, y6), respectively. Japanese Patent Publication No. HEI 8-49653 describes an exemplary change in force (fi) relative to a piston stroke phase in compressor (A). As shown in FIG. 2, the resultant anti-compressive force (F) acts onhinge mechanism 9 and is shown at a representative position (R). Resultant force (F) and position (R) may be represented by Cartesian coordinates (XR, YR), such that the following formulas are satisfied: - XR=(Σfi*xi)/Σfi; (1)
- YR=(Σf1* yi)/Σfi; and (2)
- F=Σfi, in which (i) equals 1-6. (3)
- The mechanical load on compressor (A) depends on a difference between a discharge pressure of the refrigerant and a suction pressure of the refrigerant. Moreover, the discharge pressure of the refrigerant and the suction pressure of the refrigerant depend on a thermal load on the air conditioning system, and the thermal load on the air conditioning system depends on a temperature of the vehicle. As such, the mechanical load on compressor (A) continuously changes. When the mechanical load on compressor (A) changes, the magnitude of resultant force (F) acting on
hinge mechanism 9 viaswash plate 3 also changes. Specifically, when the mechanical load on compressor (A) decreases, result force (F) also decreases, and position (R) moves towardsaxis 20 ofdrive shaft 1. Similarly, when the mechanical load on compressor (A) increases, result force (F) also increases, and position (R) moves away fromaxis 20 ofdrive shaft 1. Thus, when the mechanical load on compressor (A) changes between a minimum mechanical load and a maximum mechanical load, position (R) at which resultant force (F) acts onswash plate 3 moves from a first portion (t1) of a force line (t) to a second portion (t2) of force line (t). Second portion (t2) of force line (t) is located further fromaxis 20 ofdrive shaft 1 than first portion (t1) of force line (t), and force line (t) is defined as a set of positions (R) in plane II at which resultant force (F) may be located. According to a computer simulation, force line (t) is a substantially straight line and a first end of first portion (t1) of force line (t) intersects axis (y) to form an acute angle θ having a value between about 15° and about 25°. Nevertheless, it will be understood by those of ordinary skill in the art that the value of angle θ depends on the number ofcylinder bores 6 a formed withincylinder block 6 and the properties of the refrigerant used in the compressor. - When the mechanical load on compressor (A) is less than a predetermined mechanical load, position (R), at which resultant force (F) acts on
swash plate 3, is located along first portion (t1) of force line (t). Moreover, the resultant force (F) acts onhinge mechanism 9 viaswash plate 3 by each of the pair of rotor arms 2 a. Specifically, resultant force (F) acts onhinge mechanism 9 by a first rotor arm 2 a 1 and a second rotor arm 2 a 2. Similarly, when the mechanical load on compressor (A) is greater than the predetermined mechanical load, position (R) at which resultant force (F) acts onswash plate 3, is located along second portion (t2) of force line (t). Nevertheless, the resultant force (F) acts onhinge mechanism 9 viaswash plate 3 substantially by first rotor arm 2 a 1. Consequently, when the mechanical load on compressor (A) is at a maximum, the maximum resultant force (F) acts onhinge mechanism 9 substantially by one of rotor arms 2 a. - Therefore, a need has arisen for swash plate-type, variable displacement compressors which overcome these and other short comings of the related art. A technical advantage of the present invention is that the number of parts may be reduced without decreasing performance of the compressors. Specifically, a rotor may comprise a single rotor arm having an oblong hole formed therethrough, and a swash plate may comprise a single swash plate arm having a pin extending therefrom. Consequently, another technical advantage of the present invention is that the manufacturing cost of each of the compressors may be reduced without decreasing performance of the compressors.
- According to an embodiment of the present invention, a swash plate-type, variable displacement compressor is described. The compressor comprises a front housing, a cylinder block, a rear housing, and a drive shaft rotatably supported by the front housing and by the cylinder block. A plurality of cylinder bores are formed within the cylinder block. The compressor also comprises a rotor fixed to the drive shaft, such that the rotor and the drive shaft rotate together, and a plurality of pistons, each of which is slidably positioned within a corresponding cylinder bore. The compressor further comprises a swash plate having a penetration hole formed through a center portion of the swash plate, such that the drive shaft extends through the penetration hole. Moreover, the swash plate is connected to each of the pistons by a pair of shoes. The compressor also comprises a hinge mechanism which connects the rotor to the swash plate, such that a tilt angle of the swash plate varies with respect to an axis of rotation of the drive shaft. The hinge mechanism comprises a single rotor arm having an oblong hole formed therethrough, and a single swash plate arm having a pin portion extending therefrom, such that the pin portion slidably engages an inner wall of the oblong hole. When a mechanical load of the compressor is greater than a predetermined mechanical load, a resultant force of the mechanical load is located at a point along a first portion of a force line, and an area of engagement between a surface of the pin portion and the inner wall of the oblong hole comprises the first portion of the force line.
- Other objects, features, and advantages will be apparent to persons of ordinary skill in the art in view of the following detailed description of the invention and the accompanying drawings.
- For a more complete understanding of the present invention, the needs satisfied thereby, and the features and advantages thereof, reference now is made to the following descriptions taken in connection with the accompanying drawings.
- FIG. 1 is a cross-sectional view of a known, swash plate-type, variable displacement compressor.
- FIG. 2 is a partial, cross-sectional view of the compressor of FIG. 1 taken along a line II-II in a direction (Z).
- FIG. 3 is a cross-sectional view of a swash plate-type, variable displacement compressor according to an embodiment of the present invention.
- FIG. 4 is a partial, cross-sectional view of the compressor of FIG. 3 taken along a line IV-IV in a direction (Z).
- Preferred embodiments of the present invention and their advantages may be more readily understood by referring to FIGS. 3 and 4, like numerals being used for like corresponding parts in the various drawings.
- Referring to FIG. 3 a swash plate-type, variable displacement compressor (A′) for use in an air conditioning system of a vehicle (not shown) according to an embodiment of the present invention is depicted. Compressor (A′) may comprise a
front housing 7, acylinder block 6, arear housing 8, and adrive shaft 1.Front housing 7,cylinder block 6, andrear housing 8 may be fixably attached by a plurality ofbolts 15. Driveshaft 1 may pass through the center offront housing 7 and the center ofcylinder block 6. Driveshaft 1 also may be rotatably supported byfront housing 7 and bycylinder block 6 via a pair of bearing 11 and 12 mounted infront housing 7 andcylinder block 6, respectively. A plurality of cylinder bores 6 a may be formed withincylinder block 6 and also may be positioned equiangularly around an axis ofrotation 20 ofdrive shaft 1. Moreover, apiston 5 may be slidably positioned within each cylinder bore 6 a, such thatpistons 5 reciprocate along axes parallel to anaxis 20 ofdrive shaft 1. - Compressor (A′) also may comprise a
rotor 2, acrank chamber 30, and aswash plate 3. Specifically,rotor 2 is fixed to driveshaft 1, such thatdrive shaft 1 androtor 2 rotate together. Crankchamber 30 is formed betweenfront housing 7 andcylinder block 6, andswash plate 3 may be positioned inside crankchamber 30.Swash plate 3 may be slidably connected to eachpiston 5 via a pair ofshoes 4 positioned betweenswash plate 3 and each ofpistons 5.Swash plate 3 may include apenetration hole 3c formed therethrough at a center portion ofswash plate 3, and driveshaft 1 may extend throughpenetration hole 3 c.Rotor 2 may comprise a single rotor arm 2 a′ and anoblong hole 2 b′ formed through rotor arm 2 a′, andswash plate 3 further may comprise a single swash plate arm 3 a′ and apin 3 b′ extending from swash plate arm 3 a′. Ahinge mechanism 9′ may comprise rotor arm 2 a′, swash plate arm 3 a′,oblong hole 2 b′, andpin 3 b′, androtor 2 may be connected toswash plate 3 byhinge mechanism 9′. Specifically,pin 3 b′ may be inserted into and may slidably engage an inner wall ofoblong hole 2 b′. Moreover, becausepin 3 b′ may move withinoblong hole 2 b′, the tilt angle ofswash plate 3 may be varied with respect to driveshaft 1, such that the fluid displacement of compressor (A′) also may be varied. - Compressor (A′) also may comprise an electromagnetic clutch (not shown). When the electromagnetic clutch is activated, an external driving force from an external driving source (not shown) is transmitted to drive
shaft 1, such thatdrive shaft 1,rotor 2, andswash plate 3 rotate substantially simultaneously aboutaxis 20 ofdrive shaft 1. Moreover,swash plate 3 also moves back and forth in a wobbling motion, such that only movement in a direction parallel toaxis 20 ofdrive shaft 1 is transferred fromswash plate 3 topistons 5. Consequently, eachpiston 5 reciprocates within its corresponding cylinder bore 6 a and compresses a fluid, eg., a refrigerant, within acompression chamber 50 formed by a top portion ofpiston 5, the walls of cylinder bore 6 a, and avalve plate 40. - Referring to FIG. 4, a partial, cross-sectional view of compressor (A′) taken along a line IV-IV in a direction (Z) is depicted. A plane II includes a first axis (x) and a second axis (y), in which second axis (y) includes
axis 20 ofdrive shaft 1 and first axis (x) is perpendicular to axis (y). Plane II also includes an upper dead center portion (P) ofswash plate 3. Moreover, in compressor (A′), cylinder bores 6 a comprise a first cylinder bore 6 a 1, a second cylinder bore 6 a 2, a third cylinder bore 6 a 3, a fourth cylinder bore 6 a 4, a fifth cylinder bore 6 a 5, and a sixth cylinder bore 6 a 6. Whenpistons 5 reciprocate within corresponding cylinder bores 6 a 1-6 a 6, respectively, each ofpistons 5 apply an anti-compressive force onswash plate 3. Specifically,pistons 5 apply anti-compressive forces (f1), (f2), (f3), (f4), (f5), and (f6) onswash plate 3 at positions (x1, y1), (x2, y2), (x3, y3) (x4, y4), (x5, y5), and (x6, y6), respectively. Referring to FIG. 4, resultant anti-compressive force (F) acts onhinge mechanism 9′ and is shown at a representative position (R). Resultant force (F) and position (R) may be represented by Cartesian coordinates (XR, YR), such that the following formulas are satisfied: - XR=(Σfi*xi)/Σfi; (1)
- YR=(Σfi*yi)/Σfi; and (2)
- F=Σf1, in which (i) equals 1, 2, 3, 4, 5, and 6. (3)
- The mechanical load on compressor (A′) depends on a difference between a discharge pressure of the refrigerant and a suction pressure of the refrigerant. Moreover, the discharge pressure of the refrigerant and the suction pressure of the refrigerant depend on a thermal load on the air conditioning system, and the thermal load on the air conditioning system depends on a temperature of the vehicle. As such, the mechanical load on compressor (A′) continuously changes. When the mechanical load on compressor (A′) changes, the magnitude of resultant force (F) acting on
hinge mechanism 9′ viaswash plate 3 also changes. Specifically, when the mechanical load on compressor (A′) decreases, resultant force (F) also decreases, and position (R) moves towardsaxis 20 ofdrive shaft 1. Similarly, when the mechanical load on compressor (A′) increases, resultant force (F) also increases, and position (R) moves away fromaxis 20 ofdrive shaft 1. Thus, when the mechanical load on compressor (A′) changes between a minimum mechanical load and a maximum mechanical load, position (R) at which resultant force (F) acts onswash plate 3 moves from a first portion (t1) of a force line (t) to a second portion (t2) of force line (t). Second portion (t2) of force line (t) is located further fromaxis 20 ofdrive shaft 1 than first portion (t1) of force line (t), and force line (t) is defined as a set of positions (R) in plane II at which resultant force (F) may be located. According to a computer simulation, force line (t) is a substantially straight line and a first end of first portion (t1) of force line (t) intersects axis (y) to form an acute angle θ having a value between about 15° and about 25°. Nevertheless, it will be understood by those of ordinary skill in the art that the value of angle θ depends on the number of cylinder bores 6 a formed withincylinder block 6 and the properties of the refrigerant used in the compressor. - When the mechanical load on compressor (A′) is less than a predetermined mechanical load, position (R) at which resultant force (F) acts on
swash plate 3 is located along first portion (t1) of force line (t). Moreover, the resultant force (F) acts onhinge mechanism 9′ viaswash plate 3 by rotor arm 2 a′. Similarly, when the mechanical load on compressor (A′) is greater than the predetermined mechanical load, position (R) at which resultant force (F) acts onswash plate 3 is located along second portion (t2) of force line (t). Further, the resultant force (F) acts onhinge mechanism 9′ viaswash plate 3 by rotor arm 2 a′. A region (S) is defined as an area of engagement between a surface ofpin 3 b′ and the inner wall ofoblong hole 2 b′ in plane II.Hinge mechanism 9′ may support a greater resultant force (F) when position (R) of resultant force (F) is inside region (S) than when position (R) is outside region (S). In one embodiment, a size ofhinge mechanism 9′ may be selected, such that region (S) substantially or entirely includes portion (t2) of force line (t). When the mechanical load on compressor (A′) is less than the predetermined mechanical load, position (R) of resultant force (F) is outside region (S). Nevertheless, because position (R) of resultant force (F) lies outside region (S) only when the mechanical load of compressor (A′) is less than the predetermined mechanical load, the mechanical load of compressor (A′) may be supported by a single rotor arm and a single swash plate arm, without degrading compressor performance. - While the invention has been described in connection with preferred embodiments, it will be understood by those skilled in the art that other variations and modifications of the preferred embodiments described above may be made without departing from the scope of the invention. Other embodiments will be apparent to those skilled in the art from a consideration of the specification or practice of the invention disclosed herein. It is intended that the specification and the described examples are considered as exemplary.
Claims (4)
1. A swash plate-type, variable displacement compressor comprising:
a front housing;
a cylinder block, wherein a plurality of cylinder bores are formed within said cylinder block;
a rear housing;
a drive shaft rotatably supported by said front housing and by said cylinder block;
a rotor fixed to said drive shaft, such that said rotor and said drive shaft rotate together;
a plurality of pistons, each of which is slidably positioned within a corresponding cylinder bore;
a swash plate having a penetration hole formed through a center portion of said swash plate, wherein said drive shaft extends through said penetration hole and said swash plate is connected to each of said pistons by a pair of shoes; and
a hinge mechanism connecting said rotor to said swash plate, such that a tilt angle of said swash plate varies with respect to an axis of rotation of said drive shaft, wherein said hinge mechanism comprises:
a single rotor arm having an oblong hole formed therethrough; and
a single swash plate arm having a pin portion extending therefrom, wherein said pin portion slidably engages an inner wall of said oblong hole, and when a mechanical load of said compressor is greater than a predetermined mechanical load, a resultant force of said mechanical load is located at a point along a first portion of a force line, wherein an area of engagement between a surface of said pin portion and said inner wall of said oblong hole comprises said first portion of said force line.
2. The compressor of claim 1 , wherein when a mechanical load of said compressor is less than said predetermined mechanical load, said resultant force of said mechanical load is located at a point along a second portion of said force line.
3. The compressor of claim 2 , wherein said second portion of said force line is substantially outside said area of engagement between said surface of said pin portion and said inner wall of said oblong hole.
4. The compressor of claim 2 , wherein said second portion of said force line is entirely outside said area of engagement between said surface of said pin portion and said inner wall of said oblong hole.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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JPP2001-108803 | 2001-04-06 | ||
JP2001108803A JP2002303261A (en) | 2001-04-06 | 2001-04-06 | Variable displacement swash plate compressor |
Publications (1)
Publication Number | Publication Date |
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US20020144591A1 true US20020144591A1 (en) | 2002-10-10 |
Family
ID=18960875
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US10/095,039 Abandoned US20020144591A1 (en) | 2001-04-06 | 2002-03-12 | Swash plate-type variable displacement compressors |
Country Status (4)
Country | Link |
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US (1) | US20020144591A1 (en) |
JP (1) | JP2002303261A (en) |
DE (1) | DE10214149A1 (en) |
FR (1) | FR2823261B1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110041682A1 (en) * | 2006-09-08 | 2011-02-24 | Hiroyuki Makishima | Variable capacity compressor |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6186048B1 (en) * | 1998-01-13 | 2001-02-13 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63192971A (en) * | 1987-02-04 | 1988-08-10 | Hitachi Ltd | Variable stroke type compressor |
KR880005363A (en) * | 1986-10-01 | 1988-06-28 | 미타 가츠시게 | Variable displacement compressor |
JPH04164167A (en) * | 1990-10-26 | 1992-06-09 | Toyota Autom Loom Works Ltd | Supporting structure for swingable swash plate of swingable swash plate type variable capacity compressor |
JPH06264865A (en) * | 1993-03-12 | 1994-09-20 | Sanden Corp | Variable-displacement swash plate compressor |
JPH10266952A (en) * | 1997-03-25 | 1998-10-06 | Zexel Corp | Variable displacement type swash plate compressor |
JPH11280645A (en) | 1998-03-27 | 1999-10-15 | Sanden Corp | Variable capacity swash plate type compressor |
JP2001200783A (en) | 1999-11-09 | 2001-07-27 | Sanden Corp | Connecting structure for rotor and swash plate in variable capacity swash plate type compressor |
-
2001
- 2001-04-06 JP JP2001108803A patent/JP2002303261A/en active Pending
-
2002
- 2002-03-12 US US10/095,039 patent/US20020144591A1/en not_active Abandoned
- 2002-03-28 DE DE10214149A patent/DE10214149A1/en not_active Ceased
- 2002-04-02 FR FR0204066A patent/FR2823261B1/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6186048B1 (en) * | 1998-01-13 | 2001-02-13 | Kabushiki Kaisha Toyoda Jidoshokki Seisakusho | Variable displacement compressor |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110041682A1 (en) * | 2006-09-08 | 2011-02-24 | Hiroyuki Makishima | Variable capacity compressor |
Also Published As
Publication number | Publication date |
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JP2002303261A (en) | 2002-10-18 |
FR2823261A1 (en) | 2002-10-11 |
FR2823261B1 (en) | 2007-03-02 |
DE10214149A1 (en) | 2002-10-24 |
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Owner name: SANDEN CORPORATION, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SHIINA, MASAKI;REEL/FRAME:013033/0178 Effective date: 20020308 |
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STCB | Information on status: application discontinuation |
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