US20150184646A1 - Suction throttle mechanism of compressor - Google Patents
Suction throttle mechanism of compressor Download PDFInfo
- Publication number
- US20150184646A1 US20150184646A1 US14/551,308 US201414551308A US2015184646A1 US 20150184646 A1 US20150184646 A1 US 20150184646A1 US 201414551308 A US201414551308 A US 201414551308A US 2015184646 A1 US2015184646 A1 US 2015184646A1
- Authority
- US
- United States
- Prior art keywords
- valve
- valve body
- suction
- valve seat
- throttle mechanism
- 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
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
-
- 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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/10—Valves; Arrangement of valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1831—Valve-controlled fluid connection between crankcase and suction chamber
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7904—Reciprocating valves
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T137/00—Fluid handling
- Y10T137/7722—Line condition change responsive valves
- Y10T137/7837—Direct response valves [i.e., check valve type]
- Y10T137/7904—Reciprocating valves
- Y10T137/7922—Spring biased
Definitions
- the present invention relates to a suction throttle mechanism of a compressor.
- a variable-displacement type compressor controlling its displacement is known.
- Such a compressor includes a suction throttle mechanism.
- the suction throttle mechanism is disposed in a suction passage between an inlet port and a suction chamber.
- the suction throttle mechanism varies the opening of the suction passage. When a sucked refrigerant has a low flow rate, noise due to pulsation is likely to occur.
- the suction throttle mechanism varies the opening of the suction passage depending on the flow rate of a sucked refrigerant to thereby suppress occurrence of pulsation.
- a common suction throttle mechanism of a compressor includes a valve body (spool) for opening/closing a suction passage, and tubular guide means (housing or the like) for guiding the valve body. While the valve body is reciprocating, the valve body is guided by the guide means. The valve body is moved away from a valve seat to open a valve hole and thereby allow an inlet port and a suction chamber to communicate with each other through the suction passage. Depending on the amount of displacement (amount of lift) of the valve body, the opening of the suction passage is adjusted.
- the compressor disclosed in Japanese Patent Laying-Open No. 2008-196465 includes a housing, a suction passage provided to extend through the housing, and a suction throttle valve disposed inside the suction passage.
- the suction throttle valve includes a hollow-cylindrical valve housing and a valve body disposed in an internal space (valve chamber) of the valve housing and reciprocating while sliding in contact with the inner peripheral surface of the valve housing.
- a communication passage (through hole) is also provided to extend therethrough for allowing the valve chamber and a suction chamber to communicate with each other.
- a refrigerant flowing from an inlet port into the valve chamber through a valve hole further flows through the communication passage toward the suction chamber.
- the valve housing has a function for forming the communication passage in addition to a function of guiding the valve body.
- an increase of the opening area of the communication passage involves an increase of the size of the through hole provided to extend through the guide means such as the valve housing.
- This also involves a decrease of the size of a portion (sidewall) of the guide means, namely the portion guiding the valve body. While the aforementioned portion of the guide means that guides the valve body acts as a resistance against the flow of the refrigerant, this portion still requires a certain strength or more. It has conventionally been difficult to decrease the portion of the guide means that guides the valve body, namely to increase the opening area of the communication passage.
- An object of the present invention is to provide a suction throttle mechanism of a compressor that has a structure enabling the opening area of the communication passage to be increased.
- a suction throttle mechanism of a compressor based on the present invention includes: a valve seat disposed in a suction passage between an inlet port and a suction chamber of the compressor and formed in a cylindrical shape for passing a fluid through the valve seat; a valve body moving in the suction passage in a contact-separate direction in which the valve body is to contact or separate from the valve seat to thereby adjust an opening of the suction passage; and a valve housing accommodating an urge member urging the valve body toward the valve seat, the valve housing and the valve seat being formed as separate bodies, the valve housing and the valve seat being spaced away from each other, the valve housing having a guide portion sliding in contact with the valve body to thereby allow the valve body to move in the contact-separate direction.
- the present invention can implement a structure that enables the opening area of the communication passage to be increased.
- FIG. 1 is a cross-sectional view showing a compressor including a suction throttle mechanism in a first embodiment.
- FIG. 2 is a cross-sectional view showing the suction throttle mechanism (closed state) in the first embodiment.
- FIG. 3 is a perspective view schematically showing the suction throttle mechanism (opened state) in the first embodiment.
- FIG. 4 is a cross-sectional view showing the suction throttle mechanism (full-opened state) in the first embodiment.
- FIG. 5 is a cross-sectional view along a line V-V in FIG. 4 as seen in the direction of arrows.
- FIG. 6 is a cross-sectional view showing a suction throttle mechanism (full-opened state) in a comparative example.
- FIG. 7 is a cross-sectional view along a line VII-VII in FIG. 6 as seen in the direction of arrows.
- FIG. 8 is a cross-sectional view showing a suction throttle mechanism (closed state) in a second embodiment.
- FIG. 9 is a cross-sectional view showing a suction throttle mechanism (closed state) in a third embodiment.
- FIG. 10 is a perspective view schematically showing a suction throttle mechanism (opened state) in a fourth embodiment.
- FIG. 1 is a cross-sectional view showing a variable-displacement-type swash plate compressor 100 (hereinafter referred to as compressor).
- a suction throttle mechanism 50 of the compressor in the present embodiment (hereinafter referred to as suction throttle mechanism 50 ) is included in this compressor 100 (as will be detailed later herein).
- the compressor 100 includes a housing 11 which forms an outer shell of the compressor 100 .
- the housing 11 includes a cylinder block 12 , a front housing 13 , and a rear housing 14 .
- the front housing 13 is joined.
- the rear housing 14 is joined.
- the cylinder block 12 , the front housing 13 , and the rear housing 14 are fastened together with a bolt 15 which is passed through from the front housing 13 to the rear housing 14 .
- a crank chamber 16 is formed in the inside of the front housing 13 .
- the rear side of the crank chamber 16 is closed by the cylinder block 12 .
- a driveshaft 17 In the crank chamber 16 , a driveshaft 17 , a lug plate 21 , and a swash plate 22 are provided in the crank chamber 16 .
- the driveshaft 17 passes through a substantially central portion of the crank chamber 16 and extends in the fore-and-aft direction.
- the driveshaft 17 is rotatably supported by a radial bearing 18 provided in the front housing 13 and a radial bearing 19 provided in the cylinder block 12 .
- a shaft seal mechanism 20 Located forward of the radial bearing 18 is a shaft seal mechanism 20 .
- the shaft seal mechanism 20 makes sliding contact with the outer peripheral surface of the driveshaft 17 .
- the front end of the driveshaft 17 is coupled through a power transmission mechanism (not shown) to an external drive source.
- the lug plate 21 in the crank chamber 16 is fixed to the driveshaft 17 , and rotates together with the driveshaft 17 .
- the swash plate 22 is disposed rearward of the lug plate 21 .
- a hinge mechanism 23 is provided between the lug plate 21 and the swash plate 22 .
- the swash plate 22 forms a part of a displacement changing mechanism, and is supported in such a manner that the swash plate can slide and can tilt in the axial direction of the driveshaft 17 .
- the swash plate 22 is coupled to the lug plate 21 and the driveshaft 17 through the hinge mechanism 23 so that the swash plate is synchronously rotatable and tiltable.
- a coil spring 24 and a tubular body 25 are provided between the lug plate 21 and the swash plate 22 .
- the tubular body 25 is freely slidable along the driveshaft 17 , and urged rearward by the coil spring 24 .
- the swash plate 22 is constantly pressed by the coil spring 24 and the tubular body 25 , in the direction in which the tilt angle of the swash plate 22 is decreased.
- the tilt angle of the swash plate 22 is the angle formed between a plane orthogonal to the driveshaft 17 and the swash plate 22 .
- the attitude (position) of the swash plate 22 when the swash plate 22 forms a maximum tilt angle is determined by abutment of a front end 22 a of the swash plate 22 against the lug plate 21 .
- a coil spring 27 and a snap ring 26 are provided rearward of the swash plate 22 .
- the snap ring 26 is mounted on the driveshaft 17 .
- the attitude (position) of the swash plate 22 when the swash plate 22 forms a minimum tilt angle is determined by abutment of the swash plate 22 against the coil spring 27 .
- the swash plate 22 indicated by a solid line forms the maximum tilt angle
- the swash plate 22 indicated by a phantom line forms the minimum tilt angle.
- a plurality of cylinder bores 12 a are formed in the inside of the cylinder block 12 .
- a single-headed piston 28 is accommodated in each cylinder bore 12 a.
- Each piston 28 has its neck where a recess 28 a is formed.
- a pair of shoes 29 a, 29 b is accommodated in the recess 28 a.
- An outer peripheral portion 22 b of the swash plate 22 is disposed between the shoes 29 a, 29 b.
- the swash plate 22 is swung, and each piston 28 is reciprocated in the fore-and-aft direction in the cylinder bore 12 a through the shoes 29 a, 29 b.
- the rear side of the cylinder block 12 and the front side of the rear housing 14 are joined to each other with a valve plate 31 interposed therebetween.
- a suction port 31 a and a discharge port 31 b are provided in the valve plate 31 .
- a suction chamber 32 is formed on the central side.
- a discharge chamber 33 is formed on the peripheral side. The suction chamber 32 communicates through the suction port 31 a with a compression chamber 30 in the cylinder bore 12 a, and the discharge chamber 33 communicates through the discharge port 31 b with the compression chamber 30 in the cylinder bore 12 a.
- the suction port 31 a and the discharge port 31 b are provided with a suction valve 31 c and a discharge valve 31 d , respectively. While the piston 28 is moved from a top dead center position to a bottom dead center position, a refrigerant gas in the suction chamber 32 is sucked through the suction port 31 a into the compression chamber 30 . The refrigerant gas sucked into the compression chamber 30 is compressed by a movement of the piston 28 from the bottom dead center position to the top dead center position, and discharged through the discharge port 31 b into the discharge chamber 33 .
- a displacement control valve 34 is placed in the rear housing 14 .
- the displacement control valve 34 changes the tilt angle of the swash plate 22 .
- the displacement control valve 34 is disposed at a certain position along a supply passage 35 which allows the crank chamber 16 and the discharge chamber 33 to communicate with each other.
- a bleed passage 36 which allows the crank chamber 16 and the suction chamber 32 to communicate with each other is formed.
- the opening of the displacement control valve 34 is adjusted and accordingly the pressure in the crank chamber 16 is determined depending on the relation between the amount of a high-pressure refrigerant gas drawn from the discharge chamber 33 into the crank chamber 16 and the amount of the refrigerant gas drawn out through the bleed passage 36 from the crank chamber 16 to the suction chamber 32 .
- a pressure difference between the inside of the crank chamber 16 and the inside of the compression chamber 30 is changed and accordingly the tilt angle of the swash plate 22 is changed.
- the tilt angle of the swash plate 22 is thus changed. Accordingly the amount of stroke of the piston 28 is adjusted and the displacement of the compressor 100 is also adjusted.
- a suction passage 38 is provided to extend therethrough for taking in a refrigerant gas.
- the suction passage 38 is formed in a substantial L shape having a bent portion, and an inlet port 37 is arranged at an inlet portion of the suction passage 38 .
- the inlet port 37 is connected to a low-pressure side of an external refrigerant circuit (not shown).
- an external refrigerant circuit not shown.
- a suction throttle mechanism 50 is provided for changing the opening of the suction passage 38 .
- FIG. 2 is a cross-sectional view showing the suction throttle mechanism 50 (closed state), the suction passage 38 , and some other parts.
- FIG. 3 is a perspective view schematically showing the suction throttle mechanism 50 (opened state).
- FIG. 4 is a cross-sectional view showing the suction throttle mechanism 50 (full-opened state), the suction passage 38 , and some other parts.
- FIG. 5 is a cross-sectional view along a line V-V in FIG. 4 as seen in the direction of arrows.
- the suction passage 38 is a space formed by making a part of the rear housing 14 hollow, and has a portion (cylindrical space) extending in the shape of a cylinder from the inlet port 37 to a bottom 38 a.
- a hollow portion 42 is further provided for allowing the cylindrical space and the suction chamber 32 to communicate with each other.
- the suction passage 38 has a substantial L shape made up of the cylindrical space and the hollow portion 42 .
- the hollow portion 42 is formed by making a hole in a wall-like part of the rear housing 14 that is located between the suction chamber 32 and the portion (cylindrical portion) extending in the shape of a cylinder from the inlet port 37 to the bottom 38 a (in the part corresponding to the sidewall of the cylindrical space), so that the hole extends from the suction chamber 32 toward the cylindrical space.
- the aforementioned cylindrical space may be provided in the rear housing 14 after the suction chamber 32 and the hollow portion 42 are provided in the rear housing 14 .
- the hollow portion 42 is a space extending in the shape of a cylinder from the suction chamber 32 toward a bottom 42 a, and this space crosses the cylindrical space (the portion extending in the shape of a cylinder from the inlet port 37 to the bottom 38 a ).
- the hollow portion 42 is formed to extend from the suction chamber 32 to a position beyond the portion where the cylindrical space is formed.
- the bottom 42 a of the hollow portion 42 is located away from the suction throttle mechanism 50 (such as a valve housing 58 ) (see FIG. 5 ), and the bottom 42 a of the hollow portion 42 faces to the suction throttle mechanism 50 with a space therebetween.
- the suction throttle mechanism 50 disposed in the suction passage 38 includes a valve body 52 , a valve seat 54 , a coil spring 56 ( FIG. 2 ), and the valve housing 58 .
- the valve seat 54 and the valve housing 58 are fit in the bent portion of the suction passage 38 so that they face to each other.
- the valve seat 54 has a hollow-cylindrical shape whose center is an axial line X 1 , and is disposed in the suction passage 38 between the inlet port 37 and the suction chamber 32 of the compressor 100 .
- a valve hole 54 h is formed inside the valve seat 54 , and a refrigerant (fluid) passes through the valve hole 54 h (in the valve seat 54 ).
- a seat surface 54 b is formed at the lower end of the valve seat 54 .
- the seat surface 54 b is located on a plane which is in parallel with a plane orthogonal to the axial line X 1 .
- the seat surface 54 b is provided to be closer to the inlet port 37 than the valve body 52 and restricts movement of the valve body 52 displaced toward the inlet port 37 .
- four engage pieces 54 a are provided.
- the valve seat 54 With an O ring 55 ( FIG. 2 ) fit around the valve seat 54 , the valve seat 54 is inserted into the suction passage 38 in the direction of approaching the inlet port 37 (in the bottom-to-top direction in the drawing of FIG. 2 ).
- recesses corresponding to the engage pieces 54 a are provided in an inner peripheral surface of the rear housing 14 that forms the suction passage 38 .
- the engage pieces 54 a are engaged in the recesses to thereby prevent the valve seat 54 from coming off the rear housing 14 .
- the lower end of the valve seat 54 protrudes from the inner peripheral surface (wall surface) of the rear housing 14 where the valve seat 54 is fixed, toward the bottom 38 a of the suction passage 38 , and the seat surface 54 b is located in the hollow portion 42 .
- the valve housing 58 is a member formed as a separate body from the valve seat 54 , and includes a hollow-cylindrical portion 58 a, a peripheral wall portion 58 b (guide portion), a disk portion 58 c, and a column portion 58 d (guide portion).
- the hollow-cylindrical portion 58 a and the peripheral wall portion 58 b have a hollow-cylindrical shape whose center is the axial line X 1 .
- the peripheral wall portion 58 b has a shape extending in the direction of approaching the valve seat 54 , along the direction parallel with the direction in which the axial line X 1 extends.
- the peripheral wall portion 58 b is arranged to externally surround an outer peripheral surface 52 s of the valve body 52 .
- the peripheral wall portion 58 b makes sliding contact with the outer peripheral surface 52 s of the valve body 52 to thereby allow the valve body 52 to move in a contact-separate direction (the direction indicated by an arrow AR shown in FIG. 3 ) in which the value body 52 is to contact or separate from the value seat 54 to thereby adjust an opening of the suction passage 38 .
- the hollow-cylindrical portion 58 a is located closer to the bottom 38 a of the suction passage 38 .
- a vent hole 58 h is provided in the hollow-cylindrical portion 58 a.
- the valve housing 58 (the hollow-cylindrical portion 58 a, the peripheral wall portion 58 b, the disk portion 58 c, and the column portion 58 d ) and the valve body 52 form a valve chamber in their inside.
- the vent hole 58 h allows the valve chamber and the suction chamber 32 to communicate with each other.
- the area of the opening of the vent hole 58 h and the spring constant of the coil spring 56 or the like are changed to thereby adjust the force which is necessary for causing the refrigerant to press down the valve body 52 and open the suction passage 38 .
- the disk portion 58 c closes the lower end of the hollow-cylindrical portion 58 a.
- On the outer periphery of the disk portion 58 c four engage pieces 58 f are provided.
- the column portion 58 d has the shape of a cylindrical column.
- the column portion 58 d is provided on the disk portion 58 c and extends along the axial line X 1 .
- a leading end 58 e of the column portion 58 d has a tapered shape gradually decreasing in the direction of approaching the valve seat 54 .
- the column portion 58 d has a function of guiding the valve body 52 which moves in the contact-separate direction.
- the column portion 58 d is inserted in a through hole 52 h (as will be described later herein) formed in the valve body 52 , and makes sliding contact with the inner peripheral surface forming the through hole 52 h of the valve body 52 to thereby allow the valve body 52 to move in the contact-separate direction (the direction indicated by the arrow AR shown in FIG. 3 ) while guiding the valve body 52 .
- the column portion 58 d in the present embodiment is formed integrally with the disk portion 58 c so that it forms a part of the valve housing 58
- the column portion 58 d may be formed of another member independent of the valve housing 58 .
- valve housing 58 With an O ring 57 ( FIG. 2 ) fit around the valve housing 58 (hollow-cylindrical portion 58 a ), the valve housing 58 is inserted in the bottom 38 a side of the suction passage 38 in the direction of separating from the inlet port 37 (in the top-to-bottom direction in the drawing of FIG. 2 ).
- recesses corresponding to the engage pieces 58 f are provided in an inner peripheral surface of the rear housing 14 that forms the suction passage 38 . The engage pieces 58 f are engaged in the recesses to thereby prevent the valve housing 58 from coming off the rear housing 14 .
- valve housing 58 and the valve seat 54 are spaced away from each other.
- the upper end of the valve housing 58 protrudes from the inner peripheral surface of the rear housing 14 where the valve housing 58 is fixed, toward the inlet port 37 of the suction passage 38 .
- the leading end 58 e of the column portion 58 d extends to a position located in the valve hole 54 h of the valve seat 54 .
- the peripheral wall portion 58 b of the valve housing 58 is spaced away from the valve seat 54 .
- the upper end (called guide end 58 t ) of the peripheral wall portion 58 b of the valve housing 58 is located in the hollow portion 42 .
- the guide end 58 t is a portion of the peripheral wall portion 58 b (guide wall) that is located closest to the valve seat 54 .
- Valve body 52 is located downstream in the suction passage 38 with respect to the valve seat 54 .
- the valve body 52 moves in the suction passage 38 along the direction in which the axial line X 1 extends (the contact-separate direction to contact or separate from the valve seat 54 ) to thereby adjust the opening of the suction passage 38 .
- the valve body 52 includes an outer hollow-cylindrical portion 52 a, a disk portion 52 b , and an inner hollow-cylindrical portion 52 d.
- the disk portion 52 b faces to the valve seat 54 .
- the outer hollow-cylindrical portion 52 a and the inner hollow-cylindrical portion 52 d have a hollow-cylindrical shape whose center is the axial line X 1 , and extend from the disk portion 52 b in the contact-separate direction of the valve body 52 .
- a seal surface 52 c is formed at the front end of the disk portion 52 b.
- the seal surface 52 c is in parallel with a plane orthogonal to the axial line X 1 .
- the valve body 52 is displaced forward to cause the seal surface 52 c to abut against the seat surface 54 b of the valve seat 54 , the valve body 52 is seated on the valve seat 54 and the seal surface 52 c closes the valve hole 54 h (suction passage 38 ).
- the through hole 52 h is formed that has a shape extending along the direction in which the valve body 52 is to contact or separate from the valve seat 54 .
- the through hole 52 h is located at the upper end of an inner peripheral surface 52 u of the inner hollow-cylindrical portion 52 d.
- the outer diameter of the outer hollow-cylindrical portion 52 a (outer peripheral surface 52 s ) of the valve body 52 is substantially equal to the inner diameter of the peripheral wall portion 58 b of the valve housing 58 .
- the inner diameter of the through hole 52 h of the valve body 52 and the inner diameter of the inner hollow-cylindrical portion 52 d (inner peripheral surface 52 u ) are each substantially equal to the outer diameter of the column portion 58 d of the valve housing 58 .
- the valve body 52 can be moved in the contact-separate direction while being guided by both the peripheral wall portion 58 b and the column portion 58 d of the valve housing 58 .
- the leading end 58 e of the column portion 58 d extends in the valve hole 54 h of the valve seat 54 . Therefore, at and around the time when the valve body 52 comes to seat on the valve seat 54 , the valve body 52 is still supported by the column portion 58 d and thus can be moved smoothly all the time.
- the inner hollow-cylindrical portion 52 d has a shape extending downward from the lower surface of the disk portion 52 b. Although the inner hollow-cylindrical portion 52 d is not a requisite component, it preferably has a certain length or more so that the valve body 52 can stably move when the valve body 52 moves in the contact-distant direction while sliding in contact with the column portion 58 d.
- a seat 53 is provided, and the coil spring 56 (urge member) is provided between the disk portion 52 b of the valve body 52 and the seat 53 .
- the coil spring 56 accommodated in the valve housing 58 urges the valve body 52 in the direction in which the valve body 52 approaches the valve seat 54 .
- a stopper 59 having an annular shape is provided on the inner side of the peripheral wall portion 58 b of the valve housing 58 .
- the column portion 58 d extends inside the inner periphery of the coil spring 56 , and the column portion 58 d and the coil spring 56 enable a stable operation of the valve body 52 .
- the opening area of the suction passage 38 is the minimum area (closed state).
- the valve body 52 shown in FIG. 2 is seated on the valve seat 54 and the suction passage 38 generates the closed state.
- a portion of the outer peripheral surface 52 s of the valve body 52 that is located closest to the valve seat 54 is herein referred to as outer peripheral end 52 t.
- the upper end (called guide end 58 t ) of the peripheral wall portion 58 b of the valve housing 58 is located further from the valve seat 54 , as compared with the outer peripheral end 52 t of the valve body 52 .
- valve body 52 when the valve body 52 comes to be separated from the valve seat 54 , the valve body 52 moves in the space between the valve seat 54 and the peripheral wall portion 58 b of the valve housing 58 .
- the valve body 52 is moved away from the valve seat 54 while being guided by both the peripheral wall portion 58 b and the column portion 58 d of the valve housing 58 .
- the opening area of the suction passage 38 is the maximum area (full-opened state).
- the lower end of the valve body 52 shown in FIG. 4 abuts against the stopper 59 and the suction passage 38 generates the full-opened state.
- the upper end (guide end 58 t ) of the peripheral wall portion 58 b of the valve housing 58 is separated sufficiently from the seat surface 54 b of the valve seat 54 , and therefore, a broad communication passage 39 is formed between the seal surface 52 c of the valve body 52 and the seat surface 54 b of the valve seat 54 .
- the communication passage 39 has a shape opened by 360° along the circumference whose center is the axial line X 1 .
- a refrigerant (fluid) flows from the inlet port 37 through the valve hole 54 h of the valve seat 54 toward the valve body 52 .
- the tapered shape of the leading end 58 e of the column portion 58 d enables the refrigerant to smoothly flow along the shape of the leading end 58 e of the column portion 58 d, and the column portion 58 d is restrained from acting as a resistance against the flow of the refrigerant.
- the refrigerant can thereafter continuously flow into the suction chamber 32 through the communication passage 39 , while spreading outward in all directions orthogonal to the axial line X 1 and passing through the portion between the valve seat 54 and the valve housing 58 (peripheral wall portion 58 b ).
- the above-described features make the opening area of the communication passage 39 larger to enable the flow rate of the refrigerant to be easily increased and accordingly enable the cooling performance by the refrigerant of the compressor 100 to be improved.
- the hollow portion 42 is provided in the rear housing 14 to thereby form the communication passage 39 which is opened by 360°. It is not a requisite feature to provide the hollow portion 42 in the rear housing 14 . In the case where the hollow portion 42 is not provided in the rear housing 14 , the communication passage 39 which is opened by 360° may not be formed. Even in this case, the column portion 58 d and the peripheral wall portion 58 b of the valve housing 58 perform the guide function. Thus, the portion of the guide means that guides the valve body 52 can be reduced in size, and accordingly the opening area of the communication passage (the space corresponding to the communication passage 39 ) can be increased.
- FIG. 6 is a cross-sectional view showing a suction throttle mechanism 50 Z (full-opened state) in a comparative example.
- FIG. 7 is a cross-sectional view along a line VII-VII in FIG. 6 as seen in the direction of arrows.
- the valve housing 58 of the suction throttle mechanism 50 Z has a peripheral wall portion 58 b coupled to the lower end of the valve seat 54 .
- An upper end 58 tz of the peripheral wall portion 58 b of the valve housing 58 is located above the seat surface 54 b of the valve seat 54 .
- the valve body 52 is moved in the contact-separate direction while being guided by only the peripheral wall portion 58 b of the valve housing 58 .
- a through hole 52 k is provided to extend therethrough for allowing the suction passage 38 (valve hole 54 h ) and the suction chamber 32 to communicate with each other.
- the part of the peripheral wall portion 58 b in which the through hole 52 k is not provided forms a sidewall 52 w ( FIG. 7 ).
- a communication passage 39 z is formed between the seal surface 52 c of the valve body 52 and the seat surface 54 b of the valve seat 54 .
- the communication passage 39 z is formed in only the portion where the sidewall 52 w is not provided, and does not have a shape opened by 360° along the circumference whose center is the axial line X 1
- the sidewall 52 w is a portion for guiding the valve body 52 , and also acts as a resistance against the flow of the refrigerant. It is necessary for the sidewall 52 w to have a certain strength or more for stably guiding the valve body 52 . It is therefore difficult to reduce the size (surface area) of the sidewall 52 w, namely increase the opening area of the communication passage 39 z.
- FIG. 8 is a cross-sectional view showing the suction throttle mechanism 50 A (closed state).
- the position of the upper end (guide end 58 t ) of the peripheral wall portion 58 b of the valve housing 58 is located relatively closer to the bottom 38 a (further from the valve seat 54 ) as compared with the above-described first embodiment.
- valve body 52 is moved in the contact-separate direction while being guided all the time by both the peripheral wall portion 58 b and the column portion 58 d of the valve housing 58 .
- the valve body 52 is moved in the contact-separate direction while being guided by both the peripheral wall portion 58 b and the column portion 58 d of the valve housing 58 .
- the valve body 52 is not guided by the peripheral wall portion 58 b of the valve housing 58 .
- valve housing 58 The fact that the position of the upper end (guide end 58 t ) of the peripheral wall portion 58 b of the valve housing 58 is located relatively closer to the bottom 38 a (further from the valve seat 54 ) enables the opening area of the communication passage 39 (see FIG. 4 ) to be larger than that of the first embodiment.
- the configuration in which the valve housing 58 does not have the peripheral wall portion 58 b may also be employed. In this case, the valve body 52 is moved in the contact-separate direction while being guided by only the column portion 58 d of the valve housing 58 .
- the opening area of the communication passage 39 can further be increased accordingly.
- FIG. 9 is a cross-sectional view showing the suction throttle mechanism 50 B (closed state).
- the valve housing 58 does not include the column portion 58 d.
- the valve body 52 is moved in the contact-separate direction while being guided by only the peripheral wall portion 58 b of the valve housing 58 .
- the upper end (guide end 58 t ) of the peripheral wall portion 58 b of the valve housing 58 is located further from the valve seat 54 , as compared with the outer peripheral end 52 t of the valve body 52 .
- the above-described features make, like the first embodiment, the opening area of the communication passage 39 (see FIG. 4 ) larger to enable the flowrate of the refrigerant to easily be increased and accordingly enable the cooling performance by the refrigerant of the compressor to be improved.
- FIG. 10 is a perspective view schematically showing the suction throttle mechanism 50 C (opened state).
- the peripheral wall portion 58 b of the valve housing 58 has a hollow-cylindrical shape.
- the peripheral wall portion 58 b of the valve housing 58 has a columnar shape, and the peripheral wall portion 58 b is divided into two portions 58 b 1 , 58 b 2 . Between the portions 58 b 1 and 58 b 2 , an opening 58 u is formed.
- Two openings 58 u are formed at respective positions separated from each other by 180° in the circumferential direction of the peripheral wall portion 58 b.
- the valve housing 58 (the hollow-cylindrical portion 58 a, the peripheral wall portion 58 b, the disk portion 58 c, and the column portion 58 d ) and the valve body 52 form a valve chamber in their inside, and the openings 58 u allow the inner space (valve chamber) of the valve housing 58 and the suction chamber 32 to communicate with each other.
- the openings 58 u can perform the function of the vent hole 58 h (see FIG. 3 ) in the first embodiment.
- the above-described features also make, like the first embodiment, the opening area of the communication passage 39 (see FIG. 4 ) larger to thereby enable the flow rate of the refrigerant to be easily increased and accordingly enable the cooling performance by the refrigerant of the compressor to be improved.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Compressor (AREA)
Abstract
A suction throttle mechanism of a compressor includes a valve body, a valve seat, and a valve housing. The valve housing and the valve seat are formed as separate bodies, and the valve housing and the valve seat are spaced away from each other. The valve housing has guide portions which make sliding contact with the valve body to thereby allow the valve body to move in a contact-separate direction. When the valve body is separated from the valve seat, a fluid flowing from an inlet port toward the valve body through the valve seat passes between the valve seat and the valve housing to enter a suction chamber.
Description
- This nonprovisional application is based on Japanese Patent Application No. 2013-272348 filed on Dec. 27, 2013 with the Japan Patent Office, the entire contents of which are hereby incorporated by reference.
- 1. Field of the Invention
- The present invention relates to a suction throttle mechanism of a compressor.
- 2. Description of the Background Art
- A variable-displacement type compressor controlling its displacement is known. Such a compressor includes a suction throttle mechanism. The suction throttle mechanism is disposed in a suction passage between an inlet port and a suction chamber. The suction throttle mechanism varies the opening of the suction passage. When a sucked refrigerant has a low flow rate, noise due to pulsation is likely to occur. The suction throttle mechanism varies the opening of the suction passage depending on the flow rate of a sucked refrigerant to thereby suppress occurrence of pulsation.
- As disclosed in Japanese Patent Laying-Open Nos. 2008-196465, 2006-207465, and 2000-136776, a common suction throttle mechanism of a compressor includes a valve body (spool) for opening/closing a suction passage, and tubular guide means (housing or the like) for guiding the valve body. While the valve body is reciprocating, the valve body is guided by the guide means. The valve body is moved away from a valve seat to open a valve hole and thereby allow an inlet port and a suction chamber to communicate with each other through the suction passage. Depending on the amount of displacement (amount of lift) of the valve body, the opening of the suction passage is adjusted.
- The compressor disclosed in Japanese Patent Laying-Open No. 2008-196465 includes a housing, a suction passage provided to extend through the housing, and a suction throttle valve disposed inside the suction passage. The suction throttle valve includes a hollow-cylindrical valve housing and a valve body disposed in an internal space (valve chamber) of the valve housing and reciprocating while sliding in contact with the inner peripheral surface of the valve housing. In the sidewall of the valve housing, a communication passage (through hole) is also provided to extend therethrough for allowing the valve chamber and a suction chamber to communicate with each other. A refrigerant flowing from an inlet port into the valve chamber through a valve hole further flows through the communication passage toward the suction chamber. The valve housing has a function for forming the communication passage in addition to a function of guiding the valve body.
- In this configuration, an increase of the opening area of the communication passage involves an increase of the size of the through hole provided to extend through the guide means such as the valve housing. This also involves a decrease of the size of a portion (sidewall) of the guide means, namely the portion guiding the valve body. While the aforementioned portion of the guide means that guides the valve body acts as a resistance against the flow of the refrigerant, this portion still requires a certain strength or more. It has conventionally been difficult to decrease the portion of the guide means that guides the valve body, namely to increase the opening area of the communication passage.
- An object of the present invention is to provide a suction throttle mechanism of a compressor that has a structure enabling the opening area of the communication passage to be increased.
- A suction throttle mechanism of a compressor based on the present invention includes: a valve seat disposed in a suction passage between an inlet port and a suction chamber of the compressor and formed in a cylindrical shape for passing a fluid through the valve seat; a valve body moving in the suction passage in a contact-separate direction in which the valve body is to contact or separate from the valve seat to thereby adjust an opening of the suction passage; and a valve housing accommodating an urge member urging the valve body toward the valve seat, the valve housing and the valve seat being formed as separate bodies, the valve housing and the valve seat being spaced away from each other, the valve housing having a guide portion sliding in contact with the valve body to thereby allow the valve body to move in the contact-separate direction. When the valve body is separated from the valve seat, a fluid flowing from the inlet port toward the valve body through the valve seat passes between the valve seat and the valve housing to enter the suction chamber.
- The present invention can implement a structure that enables the opening area of the communication passage to be increased.
- The foregoing and other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description of the present invention when taken in conjunction with the accompanying drawings.
-
FIG. 1 is a cross-sectional view showing a compressor including a suction throttle mechanism in a first embodiment. -
FIG. 2 is a cross-sectional view showing the suction throttle mechanism (closed state) in the first embodiment. -
FIG. 3 is a perspective view schematically showing the suction throttle mechanism (opened state) in the first embodiment. -
FIG. 4 is a cross-sectional view showing the suction throttle mechanism (full-opened state) in the first embodiment. -
FIG. 5 is a cross-sectional view along a line V-V inFIG. 4 as seen in the direction of arrows. -
FIG. 6 is a cross-sectional view showing a suction throttle mechanism (full-opened state) in a comparative example. -
FIG. 7 is a cross-sectional view along a line VII-VII inFIG. 6 as seen in the direction of arrows. -
FIG. 8 is a cross-sectional view showing a suction throttle mechanism (closed state) in a second embodiment. -
FIG. 9 is a cross-sectional view showing a suction throttle mechanism (closed state) in a third embodiment. -
FIG. 10 is a perspective view schematically showing a suction throttle mechanism (opened state) in a fourth embodiment. - Embodiments will hereinafter be described with reference to the drawings. Where the number, quantity, or the like is mentioned, the scope of the present invention is not necessarily limited to the number, quantity or the like unless otherwise specified. The same parts and corresponding parts are denoted by the same reference numerals, and a description thereof may not be repeated.
- (Compressor 100)
-
FIG. 1 is a cross-sectional view showing a variable-displacement-type swash plate compressor 100 (hereinafter referred to as compressor). Asuction throttle mechanism 50 of the compressor in the present embodiment (hereinafter referred to as suction throttle mechanism 50) is included in this compressor 100 (as will be detailed later herein). Thecompressor 100 includes ahousing 11 which forms an outer shell of thecompressor 100. Thehousing 11 includes acylinder block 12, afront housing 13, and arear housing 14. - To the front side of the
cylinder block 12, thefront housing 13 is joined. To the rear side of thecylinder block 12, therear housing 14 is joined. Thecylinder block 12, thefront housing 13, and therear housing 14 are fastened together with abolt 15 which is passed through from thefront housing 13 to therear housing 14. - In the inside of the
front housing 13, acrank chamber 16 is formed. The rear side of thecrank chamber 16 is closed by thecylinder block 12. In thecrank chamber 16, adriveshaft 17, alug plate 21, and aswash plate 22 are provided. Thedriveshaft 17 passes through a substantially central portion of thecrank chamber 16 and extends in the fore-and-aft direction. - The
driveshaft 17 is rotatably supported by aradial bearing 18 provided in thefront housing 13 and a radial bearing 19 provided in thecylinder block 12. Located forward of the radial bearing 18 is ashaft seal mechanism 20. Theshaft seal mechanism 20 makes sliding contact with the outer peripheral surface of thedriveshaft 17. The front end of thedriveshaft 17 is coupled through a power transmission mechanism (not shown) to an external drive source. - The
lug plate 21 in thecrank chamber 16 is fixed to thedriveshaft 17, and rotates together with thedriveshaft 17. Theswash plate 22 is disposed rearward of thelug plate 21. Between thelug plate 21 and theswash plate 22, ahinge mechanism 23 is provided. Theswash plate 22 forms a part of a displacement changing mechanism, and is supported in such a manner that the swash plate can slide and can tilt in the axial direction of thedriveshaft 17. Theswash plate 22 is coupled to thelug plate 21 and thedriveshaft 17 through thehinge mechanism 23 so that the swash plate is synchronously rotatable and tiltable. - Between the
lug plate 21 and theswash plate 22, acoil spring 24 and atubular body 25 are provided. Thetubular body 25 is freely slidable along thedriveshaft 17, and urged rearward by thecoil spring 24. Theswash plate 22 is constantly pressed by thecoil spring 24 and thetubular body 25, in the direction in which the tilt angle of theswash plate 22 is decreased. The tilt angle of theswash plate 22 is the angle formed between a plane orthogonal to thedriveshaft 17 and theswash plate 22. - The attitude (position) of the
swash plate 22 when theswash plate 22 forms a maximum tilt angle is determined by abutment of afront end 22 a of theswash plate 22 against thelug plate 21. Acoil spring 27 and asnap ring 26 are provided rearward of theswash plate 22. Thesnap ring 26 is mounted on thedriveshaft 17. The attitude (position) of theswash plate 22 when theswash plate 22 forms a minimum tilt angle is determined by abutment of theswash plate 22 against thecoil spring 27. InFIG. 1 , theswash plate 22 indicated by a solid line forms the maximum tilt angle, and theswash plate 22 indicated by a phantom line forms the minimum tilt angle. - In the inside of the
cylinder block 12, a plurality of cylinder bores 12 a are formed. In each cylinder bore 12 a, a single-headedpiston 28 is accommodated. Eachpiston 28 has its neck where arecess 28 a is formed. In therecess 28 a, a pair ofshoes swash plate 22 is disposed between theshoes driveshaft 17 is rotated, theswash plate 22 is rotated synchronously with thedriveshaft 17. Theswash plate 22 is swung, and eachpiston 28 is reciprocated in the fore-and-aft direction in the cylinder bore 12 a through theshoes - The rear side of the
cylinder block 12 and the front side of therear housing 14 are joined to each other with avalve plate 31 interposed therebetween. In thevalve plate 31, asuction port 31 a and adischarge port 31 b are provided. In therear housing 14, asuction chamber 32 is formed on the central side. In therear housing 14, adischarge chamber 33 is formed on the peripheral side. Thesuction chamber 32 communicates through thesuction port 31 a with acompression chamber 30 in the cylinder bore 12 a, and thedischarge chamber 33 communicates through thedischarge port 31 b with thecompression chamber 30 in the cylinder bore 12 a. - The
suction port 31 a and thedischarge port 31 b are provided with asuction valve 31 c and adischarge valve 31 d, respectively. While thepiston 28 is moved from a top dead center position to a bottom dead center position, a refrigerant gas in thesuction chamber 32 is sucked through thesuction port 31 a into thecompression chamber 30. The refrigerant gas sucked into thecompression chamber 30 is compressed by a movement of thepiston 28 from the bottom dead center position to the top dead center position, and discharged through thedischarge port 31 b into thedischarge chamber 33. - In the
rear housing 14, adisplacement control valve 34 is placed. Thedisplacement control valve 34 changes the tilt angle of theswash plate 22. Specifically, thedisplacement control valve 34 is disposed at a certain position along asupply passage 35 which allows thecrank chamber 16 and thedischarge chamber 33 to communicate with each other. In thecylinder block 12, ableed passage 36 which allows thecrank chamber 16 and thesuction chamber 32 to communicate with each other is formed. - The opening of the
displacement control valve 34 is adjusted and accordingly the pressure in thecrank chamber 16 is determined depending on the relation between the amount of a high-pressure refrigerant gas drawn from thedischarge chamber 33 into thecrank chamber 16 and the amount of the refrigerant gas drawn out through thebleed passage 36 from thecrank chamber 16 to thesuction chamber 32. A pressure difference between the inside of thecrank chamber 16 and the inside of thecompression chamber 30 is changed and accordingly the tilt angle of theswash plate 22 is changed. The tilt angle of theswash plate 22 is thus changed. Accordingly the amount of stroke of thepiston 28 is adjusted and the displacement of thecompressor 100 is also adjusted. - (Suction Passage 38)
- In the
rear housing 14, asuction passage 38 is provided to extend therethrough for taking in a refrigerant gas. Thesuction passage 38 is formed in a substantial L shape having a bent portion, and aninlet port 37 is arranged at an inlet portion of thesuction passage 38. Theinlet port 37 is connected to a low-pressure side of an external refrigerant circuit (not shown). Through theinlet port 37 and thesuction passage 38, a refrigerant gas is sucked from the external refrigerant circuit toward thesuction chamber 32. At a certain position along thesuction passage 38, asuction throttle mechanism 50 is provided for changing the opening of thesuction passage 38. -
FIG. 2 is a cross-sectional view showing the suction throttle mechanism 50 (closed state), thesuction passage 38, and some other parts.FIG. 3 is a perspective view schematically showing the suction throttle mechanism 50 (opened state).FIG. 4 is a cross-sectional view showing the suction throttle mechanism 50 (full-opened state), thesuction passage 38, and some other parts.FIG. 5 is a cross-sectional view along a line V-V inFIG. 4 as seen in the direction of arrows. - As shown in
FIG. 2 , thesuction passage 38 is a space formed by making a part of therear housing 14 hollow, and has a portion (cylindrical space) extending in the shape of a cylinder from theinlet port 37 to a bottom 38 a. In therear housing 14, ahollow portion 42 is further provided for allowing the cylindrical space and thesuction chamber 32 to communicate with each other. Thesuction passage 38 has a substantial L shape made up of the cylindrical space and thehollow portion 42. - The
hollow portion 42 is formed by making a hole in a wall-like part of therear housing 14 that is located between thesuction chamber 32 and the portion (cylindrical portion) extending in the shape of a cylinder from theinlet port 37 to the bottom 38 a (in the part corresponding to the sidewall of the cylindrical space), so that the hole extends from thesuction chamber 32 toward the cylindrical space. The aforementioned cylindrical space may be provided in therear housing 14 after thesuction chamber 32 and thehollow portion 42 are provided in therear housing 14. - The
hollow portion 42 is a space extending in the shape of a cylinder from thesuction chamber 32 toward a bottom 42 a, and this space crosses the cylindrical space (the portion extending in the shape of a cylinder from theinlet port 37 to the bottom 38 a). Thehollow portion 42 is formed to extend from thesuction chamber 32 to a position beyond the portion where the cylindrical space is formed. In the state (the state shown inFIG. 2 ) where thesuction throttle mechanism 50 is attached to thesuction passage 38, the bottom 42 a of thehollow portion 42 is located away from the suction throttle mechanism 50 (such as a valve housing 58) (seeFIG. 5 ), and the bottom 42 a of thehollow portion 42 faces to thesuction throttle mechanism 50 with a space therebetween. - (Suction Throttle Mechanism 50)
- As shown in
FIGS. 2 and 3 , thesuction throttle mechanism 50 disposed in thesuction passage 38 includes avalve body 52, avalve seat 54, a coil spring 56 (FIG. 2 ), and thevalve housing 58. Thevalve seat 54 and thevalve housing 58 are fit in the bent portion of thesuction passage 38 so that they face to each other. - (Valve Seat 54)
- The
valve seat 54 has a hollow-cylindrical shape whose center is an axial line X1, and is disposed in thesuction passage 38 between theinlet port 37 and thesuction chamber 32 of thecompressor 100. Avalve hole 54 h is formed inside thevalve seat 54, and a refrigerant (fluid) passes through thevalve hole 54 h (in the valve seat 54). At the lower end of thevalve seat 54, aseat surface 54 b is formed. Theseat surface 54 b is located on a plane which is in parallel with a plane orthogonal to the axial line X1. Theseat surface 54 b is provided to be closer to theinlet port 37 than thevalve body 52 and restricts movement of thevalve body 52 displaced toward theinlet port 37. At the upper end of thevalve seat 54, four engagepieces 54 a are provided. - With an O ring 55 (
FIG. 2 ) fit around thevalve seat 54, thevalve seat 54 is inserted into thesuction passage 38 in the direction of approaching the inlet port 37 (in the bottom-to-top direction in the drawing ofFIG. 2 ). In an inner peripheral surface of therear housing 14 that forms thesuction passage 38, recesses corresponding to the engagepieces 54 a are provided. The engagepieces 54 a are engaged in the recesses to thereby prevent thevalve seat 54 from coming off therear housing 14. In this state, the lower end of thevalve seat 54 protrudes from the inner peripheral surface (wall surface) of therear housing 14 where thevalve seat 54 is fixed, toward the bottom 38 a of thesuction passage 38, and theseat surface 54 b is located in thehollow portion 42. - (Valve Housing 58)
- The
valve housing 58 is a member formed as a separate body from thevalve seat 54, and includes a hollow-cylindrical portion 58 a, aperipheral wall portion 58 b (guide portion), adisk portion 58 c, and acolumn portion 58 d (guide portion). The hollow-cylindrical portion 58 a and theperipheral wall portion 58 b have a hollow-cylindrical shape whose center is the axial line X1. Theperipheral wall portion 58 b has a shape extending in the direction of approaching thevalve seat 54, along the direction parallel with the direction in which the axial line X1 extends. - The
peripheral wall portion 58 b is arranged to externally surround an outerperipheral surface 52 s of thevalve body 52. Theperipheral wall portion 58 b makes sliding contact with the outerperipheral surface 52 s of thevalve body 52 to thereby allow thevalve body 52 to move in a contact-separate direction (the direction indicated by an arrow AR shown inFIG. 3 ) in which thevalue body 52 is to contact or separate from thevalue seat 54 to thereby adjust an opening of thesuction passage 38. As compared with theperipheral wall portion 58 b, the hollow-cylindrical portion 58 a is located closer to the bottom 38 a of thesuction passage 38. In the hollow-cylindrical portion 58 a, avent hole 58 h is provided. - The valve housing 58 (the hollow-
cylindrical portion 58 a, theperipheral wall portion 58 b, thedisk portion 58 c, and thecolumn portion 58 d) and thevalve body 52 form a valve chamber in their inside. Thevent hole 58 h allows the valve chamber and thesuction chamber 32 to communicate with each other. The area of the opening of thevent hole 58 h and the spring constant of thecoil spring 56 or the like are changed to thereby adjust the force which is necessary for causing the refrigerant to press down thevalve body 52 and open thesuction passage 38. Thedisk portion 58 c closes the lower end of the hollow-cylindrical portion 58 a. On the outer periphery of thedisk portion 58 c, four engagepieces 58 f are provided. - The
column portion 58 d has the shape of a cylindrical column. Thecolumn portion 58 d is provided on thedisk portion 58 c and extends along the axial line X1. A leadingend 58 e of thecolumn portion 58 d has a tapered shape gradually decreasing in the direction of approaching thevalve seat 54. Thecolumn portion 58 d has a function of guiding thevalve body 52 which moves in the contact-separate direction. - Specifically, the
column portion 58 d is inserted in a throughhole 52 h (as will be described later herein) formed in thevalve body 52, and makes sliding contact with the inner peripheral surface forming the throughhole 52 h of thevalve body 52 to thereby allow thevalve body 52 to move in the contact-separate direction (the direction indicated by the arrow AR shown inFIG. 3 ) while guiding thevalve body 52. While thecolumn portion 58 d in the present embodiment is formed integrally with thedisk portion 58 c so that it forms a part of thevalve housing 58, thecolumn portion 58 d may be formed of another member independent of thevalve housing 58. - With an O ring 57 (
FIG. 2 ) fit around the valve housing 58 (hollow-cylindrical portion 58 a), thevalve housing 58 is inserted in the bottom 38 a side of thesuction passage 38 in the direction of separating from the inlet port 37 (in the top-to-bottom direction in the drawing ofFIG. 2 ). In an inner peripheral surface of therear housing 14 that forms thesuction passage 38, recesses corresponding to the engagepieces 58 f are provided. The engagepieces 58 f are engaged in the recesses to thereby prevent thevalve housing 58 from coming off therear housing 14. - In this state, the
valve housing 58 and thevalve seat 54 are spaced away from each other. The upper end of the valve housing 58 (peripheral wall portion 58 b) protrudes from the inner peripheral surface of therear housing 14 where thevalve housing 58 is fixed, toward theinlet port 37 of thesuction passage 38. The leadingend 58 e of thecolumn portion 58 d extends to a position located in thevalve hole 54 h of thevalve seat 54. In the direction along which the axial line X1 extends (the contact-separate direction of the valve body 52), theperipheral wall portion 58 b of thevalve housing 58 is spaced away from thevalve seat 54. The upper end (calledguide end 58 t) of theperipheral wall portion 58 b of thevalve housing 58 is located in thehollow portion 42. In the direction along which the axial line X1 extends, theguide end 58 t is a portion of theperipheral wall portion 58 b (guide wall) that is located closest to thevalve seat 54. - (Valve Body 52)
Valve body 52 is located downstream in thesuction passage 38 with respect to thevalve seat 54. Thevalve body 52 moves in thesuction passage 38 along the direction in which the axial line X1 extends (the contact-separate direction to contact or separate from the valve seat 54) to thereby adjust the opening of thesuction passage 38. Thevalve body 52 includes an outer hollow-cylindrical portion 52 a, adisk portion 52 b, and an inner hollow-cylindrical portion 52 d. Thedisk portion 52 b faces to thevalve seat 54. The outer hollow-cylindrical portion 52 a and the inner hollow-cylindrical portion 52 d have a hollow-cylindrical shape whose center is the axial line X1, and extend from thedisk portion 52 b in the contact-separate direction of thevalve body 52. - At the front end of the
disk portion 52 b, aseal surface 52 c is formed. Theseal surface 52 c is in parallel with a plane orthogonal to the axial line X1. As thevalve body 52 is displaced forward to cause theseal surface 52 c to abut against theseat surface 54 b of thevalve seat 54, thevalve body 52 is seated on thevalve seat 54 and theseal surface 52 c closes thevalve hole 54 h (suction passage 38). At the center of thedisk portion 52 b, the throughhole 52 h is formed that has a shape extending along the direction in which thevalve body 52 is to contact or separate from thevalve seat 54. The throughhole 52 h is located at the upper end of an innerperipheral surface 52 u of the inner hollow-cylindrical portion 52 d. - The outer diameter of the outer hollow-
cylindrical portion 52 a (outerperipheral surface 52 s) of thevalve body 52 is substantially equal to the inner diameter of theperipheral wall portion 58 b of thevalve housing 58. The inner diameter of the throughhole 52 h of thevalve body 52 and the inner diameter of the inner hollow-cylindrical portion 52 d (innerperipheral surface 52 u) are each substantially equal to the outer diameter of thecolumn portion 58 d of thevalve housing 58. Thevalve body 52 can be moved in the contact-separate direction while being guided by both theperipheral wall portion 58 b and thecolumn portion 58 d of thevalve housing 58. In the present embodiment, the leadingend 58 e of thecolumn portion 58 d extends in thevalve hole 54 h of thevalve seat 54. Therefore, at and around the time when thevalve body 52 comes to seat on thevalve seat 54, thevalve body 52 is still supported by thecolumn portion 58 d and thus can be moved smoothly all the time. The inner hollow-cylindrical portion 52 d has a shape extending downward from the lower surface of thedisk portion 52 b. Although the inner hollow-cylindrical portion 52 d is not a requisite component, it preferably has a certain length or more so that thevalve body 52 can stably move when thevalve body 52 moves in the contact-distant direction while sliding in contact with thecolumn portion 58 d. - On the
disk portion 58 c of thevalve housing 58, aseat 53 is provided, and the coil spring 56 (urge member) is provided between thedisk portion 52 b of thevalve body 52 and theseat 53. Thecoil spring 56 accommodated in thevalve housing 58 urges thevalve body 52 in the direction in which thevalve body 52 approaches thevalve seat 54. On the inner side of theperipheral wall portion 58 b of thevalve housing 58, astopper 59 having an annular shape is provided. Thecolumn portion 58 d extends inside the inner periphery of thecoil spring 56, and thecolumn portion 58 d and thecoil spring 56 enable a stable operation of thevalve body 52. - When the
valve body 52 is lifted to the maximum extent to cause theseal surface 52 c of thevalve body 52 to abut against theseat surface 54 b of thevalve seat 54, the opening area of thesuction passage 38 is the minimum area (closed state). Thevalve body 52 shown inFIG. 2 is seated on thevalve seat 54 and thesuction passage 38 generates the closed state. In the direction along which the axial line X1 extends, a portion of the outerperipheral surface 52 s of thevalve body 52 that is located closest to thevalve seat 54 is herein referred to as outerperipheral end 52 t. In the state where thevalve body 52 is seated on thevalve seat 54, the upper end (calledguide end 58 t) of theperipheral wall portion 58 b of thevalve housing 58 is located further from thevalve seat 54, as compared with the outerperipheral end 52 t of thevalve body 52. - Referring to
FIG. 4 , when thevalve body 52 comes to be separated from thevalve seat 54, thevalve body 52 moves in the space between thevalve seat 54 and theperipheral wall portion 58 b of thevalve housing 58. Thevalve body 52 is moved away from thevalve seat 54 while being guided by both theperipheral wall portion 58 b and thecolumn portion 58 d of thevalve housing 58. When thevalve body 52 is lowered to the maximum extent and thevalve body 52 abuts against thestopper 59 in thevalve housing 58, the opening area of thesuction passage 38 is the maximum area (full-opened state). The lower end of thevalve body 52 shown inFIG. 4 abuts against thestopper 59 and thesuction passage 38 generates the full-opened state. As described above, the upper end (guideend 58 t) of theperipheral wall portion 58 b of thevalve housing 58 is separated sufficiently from theseat surface 54 b of thevalve seat 54, and therefore, abroad communication passage 39 is formed between theseal surface 52 c of thevalve body 52 and theseat surface 54 b of thevalve seat 54. - As shown in
FIGS. 4 and 5 , in the state where thevalve body 52 is separated from thevalve seat 54, thecommunication passage 39 has a shape opened by 360° along the circumference whose center is the axial line X1. When thevalve body 52 is separated from thevalve seat 54, a refrigerant (fluid) flows from theinlet port 37 through thevalve hole 54 h of thevalve seat 54 toward thevalve body 52. At this time, the tapered shape of theleading end 58 e of thecolumn portion 58 d enables the refrigerant to smoothly flow along the shape of theleading end 58 e of thecolumn portion 58 d, and thecolumn portion 58 d is restrained from acting as a resistance against the flow of the refrigerant. - The refrigerant can thereafter continuously flow into the
suction chamber 32 through thecommunication passage 39, while spreading outward in all directions orthogonal to the axial line X1 and passing through the portion between thevalve seat 54 and the valve housing 58 (peripheral wall portion 58 b). The above-described features make the opening area of thecommunication passage 39 larger to enable the flow rate of the refrigerant to be easily increased and accordingly enable the cooling performance by the refrigerant of thecompressor 100 to be improved. - In the present embodiment, the
hollow portion 42 is provided in therear housing 14 to thereby form thecommunication passage 39 which is opened by 360°. It is not a requisite feature to provide thehollow portion 42 in therear housing 14. In the case where thehollow portion 42 is not provided in therear housing 14, thecommunication passage 39 which is opened by 360° may not be formed. Even in this case, thecolumn portion 58 d and theperipheral wall portion 58 b of thevalve housing 58 perform the guide function. Thus, the portion of the guide means that guides thevalve body 52 can be reduced in size, and accordingly the opening area of the communication passage (the space corresponding to the communication passage 39) can be increased. -
FIG. 6 is a cross-sectional view showing a suction throttle mechanism 50Z (full-opened state) in a comparative example.FIG. 7 is a cross-sectional view along a line VII-VII inFIG. 6 as seen in the direction of arrows. Thevalve housing 58 of the suction throttle mechanism 50Z has aperipheral wall portion 58 b coupled to the lower end of thevalve seat 54. Anupper end 58 tz of theperipheral wall portion 58 b of thevalve housing 58 is located above theseat surface 54 b of thevalve seat 54. In the suction throttle mechanism 50Z, thevalve body 52 is moved in the contact-separate direction while being guided by only theperipheral wall portion 58 b of thevalve housing 58. - In the
peripheral wall portion 58 b, a throughhole 52 k is provided to extend therethrough for allowing the suction passage 38 (valve hole 54 h) and thesuction chamber 32 to communicate with each other. The part of theperipheral wall portion 58 b in which the throughhole 52 k is not provided forms asidewall 52 w (FIG. 7 ). When thevalve body 52 is separated from thevalve seat 54, acommunication passage 39 z is formed between theseal surface 52 c of thevalve body 52 and theseat surface 54 b of thevalve seat 54. As shown inFIG. 7 , thecommunication passage 39 z is formed in only the portion where thesidewall 52 w is not provided, and does not have a shape opened by 360° along the circumference whose center is the axial line X1 - The
sidewall 52 w is a portion for guiding thevalve body 52, and also acts as a resistance against the flow of the refrigerant. It is necessary for thesidewall 52 w to have a certain strength or more for stably guiding thevalve body 52. It is therefore difficult to reduce the size (surface area) of thesidewall 52 w, namely increase the opening area of thecommunication passage 39 z. - Referring to
FIG. 8 , asuction throttle mechanism 50A in a second embodiment will be described.FIG. 8 is a cross-sectional view showing thesuction throttle mechanism 50A (closed state). In the second embodiment, the position of the upper end (guideend 58 t) of theperipheral wall portion 58 b of thevalve housing 58 is located relatively closer to the bottom 38 a (further from the valve seat 54) as compared with the above-described first embodiment. - In the first embodiment, the
valve body 52 is moved in the contact-separate direction while being guided all the time by both theperipheral wall portion 58 b and thecolumn portion 58 d of thevalve housing 58. In the second embodiment as well, thevalve body 52 is moved in the contact-separate direction while being guided by both theperipheral wall portion 58 b and thecolumn portion 58 d of thevalve housing 58. In the state where thevalve body 52 is seated on thevalve seat 54 and the state immediately before this, however, thevalve body 52 is not guided by theperipheral wall portion 58 b of thevalve housing 58. - The fact that the position of the upper end (guide
end 58 t) of theperipheral wall portion 58 b of thevalve housing 58 is located relatively closer to the bottom 38 a (further from the valve seat 54) enables the opening area of the communication passage 39 (seeFIG. 4 ) to be larger than that of the first embodiment. The configuration in which thevalve housing 58 does not have theperipheral wall portion 58 b may also be employed. In this case, thevalve body 52 is moved in the contact-separate direction while being guided by only thecolumn portion 58 d of thevalve housing 58. The opening area of thecommunication passage 39 can further be increased accordingly. - Referring to
FIG. 9 , asuction throttle mechanism 50B in a third embodiment will be described.FIG. 9 is a cross-sectional view showing thesuction throttle mechanism 50B (closed state). In the third embodiment, thevalve housing 58 does not include thecolumn portion 58 d. Thevalve body 52 is moved in the contact-separate direction while being guided by only theperipheral wall portion 58 b of thevalve housing 58. - In the present embodiment as well, in the state where the
valve body 52 is seated on thevalve seat 54, the upper end (guideend 58 t) of theperipheral wall portion 58 b of thevalve housing 58 is located further from thevalve seat 54, as compared with the outerperipheral end 52 t of thevalve body 52. The above-described features make, like the first embodiment, the opening area of the communication passage 39 (seeFIG. 4 ) larger to enable the flowrate of the refrigerant to easily be increased and accordingly enable the cooling performance by the refrigerant of the compressor to be improved. - Referring to
FIG. 10 , asuction throttle mechanism 50C in a fourth embodiment will be described.FIG. 10 is a perspective view schematically showing thesuction throttle mechanism 50C (opened state). In the first embodiment (seeFIG. 3 ), theperipheral wall portion 58 b of thevalve housing 58 has a hollow-cylindrical shape. In the fourth embodiment, theperipheral wall portion 58 b of thevalve housing 58 has a columnar shape, and theperipheral wall portion 58 b is divided into twoportions 58b 1, 58 b 2. Between theportions 58 b 1 and 58 b 2, anopening 58 u is formed. Twoopenings 58 u are formed at respective positions separated from each other by 180° in the circumferential direction of theperipheral wall portion 58 b. The valve housing 58 (the hollow-cylindrical portion 58 a, theperipheral wall portion 58 b, thedisk portion 58 c, and thecolumn portion 58 d) and thevalve body 52 form a valve chamber in their inside, and theopenings 58 u allow the inner space (valve chamber) of thevalve housing 58 and thesuction chamber 32 to communicate with each other. Theopenings 58 u can perform the function of thevent hole 58 h (seeFIG. 3 ) in the first embodiment. - The above-described features also make, like the first embodiment, the opening area of the communication passage 39 (see
FIG. 4 ) larger to thereby enable the flow rate of the refrigerant to be easily increased and accordingly enable the cooling performance by the refrigerant of the compressor to be improved. - Although the present invention has been described and illustrated in detail, it is clearly understood that the same is by way of illustration and example only and is not to be taken by way of limitation, the scope of the present invention being interpreted by the terms of the appended claims.
Claims (9)
1. A suction throttle mechanism of a compressor, the suction throttle mechanism comprising:
a valve seat disposed in a suction passage between an inlet port and a suction chamber of the compressor and formed in a cylindrical shape for passing a fluid through the valve seat;
a valve body moving in the suction passage in a contact-separate direction in which the valve body is to contact or separate from the valve seat to thereby adjust an opening of the suction passage; and
a valve housing accommodating an urge member urging the valve body toward the valve seat,
the valve housing and the valve seat being formed as separate bodies, the valve housing and the valve seat being spaced away from each other,
the valve housing having a guide portion sliding in contact with the valve body to thereby allow the valve body to move in the contact-separate direction,
when the valve body is separated from the valve seat, a fluid flowing from the inlet port toward the valve body through the valve seat passing between the valve seat and the valve housing to enter the suction chamber.
2. The suction throttle mechanism of a compressor according to claim 1 , wherein
the valve body has a through hole provided in a direction in which the valve body is to contact or separate from the valve seat, and
the guide portion includes a column portion inserted in the through hole and making sliding contact with an inner peripheral surface of the through hole to thereby guide the valve body.
3. The suction throttle mechanism of a compressor according to claim 2 , wherein a leading end of the column portion extends in the valve seat.
4. The suction throttle mechanism of a compressor according to claim 2 , wherein a leading end of the column portion has a tapered shape gradually decreasing in a direction of approaching the valve seat.
5. The suction throttle mechanism of a compressor according to claim 2 , wherein
the urge member is a coil spring, and
the column portion extends inside an inner periphery of the coil spring.
6. The suction throttle mechanism of a compressor according to claim 2 , wherein
the valve housing, the valve body, and the column portion form a valve chamber, and
the valve housing has a vent hole formed for allowing an inside of the valve chamber to communicate with the suction chamber.
7. The suction throttle mechanism of a compressor according to claim 1 , wherein the valve body has a disk portion facing to the valve seat and a hollow-cylindrical portion extending from the disk portion in the contact-separate direction of the valve body.
8. The suction throttle mechanism of a compressor according to claim 1 , wherein the guide portion includes a peripheral wall portion which makes sliding contact with an outer peripheral surface of the valve body to thereby guide the valve body.
9. The suction throttle mechanism of a compressor according to claim 1 , wherein
the suction passage is formed in a substantial L shape having a bent portion,
the valve seat and the valve housing are fit in the bent portion of the suction passage so that the valve seat and the valve housing face to each other, and
the valve seat protrudes from a wall surface forming the suction passage.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2013-272348 | 2013-12-27 | ||
JP2013272348A JP2015124770A (en) | 2013-12-27 | 2013-12-27 | Suction throttle mechanism of compressor |
Publications (1)
Publication Number | Publication Date |
---|---|
US20150184646A1 true US20150184646A1 (en) | 2015-07-02 |
Family
ID=53372214
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/551,308 Abandoned US20150184646A1 (en) | 2013-12-27 | 2014-11-24 | Suction throttle mechanism of compressor |
Country Status (3)
Country | Link |
---|---|
US (1) | US20150184646A1 (en) |
JP (1) | JP2015124770A (en) |
DE (1) | DE102014119152A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11047373B2 (en) * | 2018-03-30 | 2021-06-29 | Kabushiki Kaisha Toyota Jidoshokki | Piston compressor including a suction throttle |
US11149722B2 (en) * | 2016-12-01 | 2021-10-19 | Sanden Automotive Components Corporation | Variable displacement refrigerant compressor having a control valve adapted to adjust an opening degree of a pressure supply passage and a switching valve in the pressure supply passage closer to a controlled pressure chamber than the control valve and switching between a first state and a second state |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1548098A (en) * | 1925-01-02 | 1925-08-04 | Pennsylvania Pump & Compressor | Cylinder relief valve |
US4241898A (en) * | 1979-01-08 | 1980-12-30 | The United States Of America As Represented By The Secretary Of The Navy | Purge valve for diver's mask |
US5080122A (en) * | 1989-10-13 | 1992-01-14 | Socla | Non-return valve |
US5636659A (en) * | 1995-10-17 | 1997-06-10 | Westinghouse Electric Corporation | Variable area compensation valve |
US7591283B2 (en) * | 2007-05-07 | 2009-09-22 | Sauer-Danfoss, Inc. | Low rise rate direct acting relief valve |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4181274B2 (en) | 1998-08-24 | 2008-11-12 | サンデン株式会社 | Compressor |
JP2006207465A (en) | 2005-01-27 | 2006-08-10 | Toyota Industries Corp | Variable displacement compressor |
JP4640351B2 (en) | 2007-02-16 | 2011-03-02 | 株式会社豊田自動織機 | Suction throttle valve for variable displacement compressor |
-
2013
- 2013-12-27 JP JP2013272348A patent/JP2015124770A/en not_active Withdrawn
-
2014
- 2014-11-24 US US14/551,308 patent/US20150184646A1/en not_active Abandoned
- 2014-12-19 DE DE102014119152.8A patent/DE102014119152A1/en not_active Ceased
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1548098A (en) * | 1925-01-02 | 1925-08-04 | Pennsylvania Pump & Compressor | Cylinder relief valve |
US4241898A (en) * | 1979-01-08 | 1980-12-30 | The United States Of America As Represented By The Secretary Of The Navy | Purge valve for diver's mask |
US5080122A (en) * | 1989-10-13 | 1992-01-14 | Socla | Non-return valve |
US5636659A (en) * | 1995-10-17 | 1997-06-10 | Westinghouse Electric Corporation | Variable area compensation valve |
US7591283B2 (en) * | 2007-05-07 | 2009-09-22 | Sauer-Danfoss, Inc. | Low rise rate direct acting relief valve |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11149722B2 (en) * | 2016-12-01 | 2021-10-19 | Sanden Automotive Components Corporation | Variable displacement refrigerant compressor having a control valve adapted to adjust an opening degree of a pressure supply passage and a switching valve in the pressure supply passage closer to a controlled pressure chamber than the control valve and switching between a first state and a second state |
US11047373B2 (en) * | 2018-03-30 | 2021-06-29 | Kabushiki Kaisha Toyota Jidoshokki | Piston compressor including a suction throttle |
Also Published As
Publication number | Publication date |
---|---|
JP2015124770A (en) | 2015-07-06 |
DE102014119152A1 (en) | 2015-07-02 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US9803628B2 (en) | Compressor with drive and tilt mechanisms located on the same side of a swash plate | |
US9581149B2 (en) | Double-headed piston type swash plate compressor | |
US9309874B2 (en) | Swash plate type variable displacement compressor | |
US9228576B2 (en) | Swash plate type variable displacement compressor | |
US9228577B2 (en) | Swash plate type variable displacement compressor | |
US9309875B2 (en) | Swash plate type variable displacement compressor | |
US9903352B2 (en) | Swash plate type variable displacement compressor | |
US8439652B2 (en) | Suction throttle valve for variable displacement type compressor | |
US20150184646A1 (en) | Suction throttle mechanism of compressor | |
US9624919B2 (en) | Variable displacement swash plate type compressor | |
US9523357B2 (en) | Variable displacement swash plate type compressor | |
US9273679B2 (en) | Variable displacement swash plate compressor | |
US20150260175A1 (en) | Variable displacement swash plate type compressor | |
US9719501B2 (en) | Swash plate type variable displacement compressor | |
US20160047367A1 (en) | Variable displacement swash-plate compressor | |
US9784259B2 (en) | Variable displacement swash plate type compressor | |
JP6135573B2 (en) | Variable capacity swash plate compressor | |
EP1930591A2 (en) | Compressor having a mechanism for separating and recovering lubrication oil | |
US9677552B2 (en) | Double-headed piston type swash plate compressor | |
US9915252B2 (en) | Variable displacement swash plate compressor having a fulcrum and an action point located on opposite sides of a drive shaft | |
US9284954B2 (en) | Variable displacement swash plate type compressor | |
US9903354B2 (en) | Variable displacement swash plate compressor | |
WO2011086907A2 (en) | Compressor | |
JP6115397B2 (en) | Variable capacity swash plate compressor | |
JP2016166532A (en) | Variable displacement double-ended swash plate compressor |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: KABUSHIKI KAISHA TOYOTA JIDOSHOKKI, JAPAN Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:FUKAZAWA, SUEHIRO;REEL/FRAME:034249/0283 Effective date: 20141107 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |