US20180073499A1 - Variable-capacity compressor - Google Patents

Variable-capacity compressor Download PDF

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Publication number
US20180073499A1
US20180073499A1 US15/561,672 US201615561672A US2018073499A1 US 20180073499 A1 US20180073499 A1 US 20180073499A1 US 201615561672 A US201615561672 A US 201615561672A US 2018073499 A1 US2018073499 A1 US 2018073499A1
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United States
Prior art keywords
chamber
passage
valve
downstream
pressure
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Abandoned
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US15/561,672
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English (en)
Inventor
Yukio Kazahaya
Masanori Amemori
Yujiro Morita
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Valeo Japan Co Ltd
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Valeo Japan Co Ltd
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Assigned to VALEO JAPAN CO., LTD. reassignment VALEO JAPAN CO., LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMEMORI, MASANORI, KAZAHAYA, YUKIO, MORITA, YUJIRO
Publication of US20180073499A1 publication Critical patent/US20180073499A1/en
Abandoned legal-status Critical Current

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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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means 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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members
    • F04B49/123—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element
    • F04B49/125—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members by changing the eccentricity of one element relative to another element by changing the eccentricity of the actuation means, e.g. cams or cranks, relative to the driving means, e.g. driving shafts
    • 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
    • F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
    • 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
    • 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
    • F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
    • F04B2027/1872—Discharge pressure

Definitions

  • the present invention relates to a variable-capacity compressor capable of varying a discharge capacity by adjusting a pressure in a control pressure chamber, and particularly relates to a variable-capacity compressor including a supply passage allowing a discharge chamber to communicate with the control pressure chamber and a bleed passage allowing the control pressure chamber to communicate with a suction chamber, in which an opening degree of the supply passage is adjusted by a control valve provided on the supply passage to thereby adjust the pressure in the control pressure chamber.
  • variable-capacity compressor adopts a mechanism in which a tilt angle of the swash plate is changed and piston stroke amounts are adjusted by adjusting the pressure of the control pressure chamber to thereby vary the discharge capacity.
  • a structure is known, in which the discharge chamber is allowed to communicate with the control pressure chamber through the supply passage, the control pressure chamber is allowed to constantly communicate with the suction chamber through the bleed passage, the opening degree of the supply passage is adjusted by the control valve provided on the supply passage and a refrigerant amount flowing into the control pressure chamber is adjusted to thereby control the pressure in the control pressure chamber.
  • the pressure in a refrigerating cycle is balanced as well as a refrigerant in the refrigerating cycle becomes liquid at a portion of the lowest temperature in the refrigerating cycle.
  • the compressor has the highest heat capacity in elements forming the refrigerating cycle and is not easily heated following variation of outdoor temperature, therefore, the phenomenon in which the refrigerant in the refrigerating cycle becomes liquid inside the compressor occurs.
  • a liquid refrigerant is accumulated also in the control pressure chamber.
  • a structure shown in FIG. 6 is known (refer to Patent Literature 1).
  • a first control valve 104 that adjusts the opening degree of a supply passage is provided on the supply passage 103 connecting between a discharge chamber 101 and a control pressure chamber 102
  • a second control valve 107 is provided on a bleed passage 106 connecting between the control pressure chamber 102 and a suction chamber 105 .
  • the second control valve 107 is configured by including a spool holding concave portion 108 formed in a housing, a spool 109 housed in the spool holding concave portion 108 so as to move, a back pressure chamber 110 demarcated and formed behind the spool 109 in the spool holding concave portion 108 , a biasing spring 112 that biases the spool 109 in a direction away from a valve forming body 111 .
  • the spool holding concave portion 108 is adjacent to the suction chamber 105 , and leakage in the spool holding concave portion 108 from the back pressure chamber 110 to the suction chamber 105 is suppressed to be small by a clearance between an inner wall of the spool holding concave portion 108 and the spool 109 .
  • a fixed throttle 113 is provided, wherein an intermediate region K between the first control valve 104 and the fixed throttle 113 is connected to the back pressure chamber 110 through a branch passage 114 .
  • the first control valve 104 makes a supply passage 28 in a fully closed state and the communicating state between the discharge chamber 101 and the control pressure chamber 102 is cut off at the time of starting when a difference between a pressure Pd in the discharge chamber 101 and a pressure Ps in the suction chamber 105 is small. Then, a pressure Pk in the intermediate region K in the supply passage 103 on the downstream side of the first control valve 104 , namely, the pressure in the back pressure chamber 110 is maintained to be approximately the same as a pressure Pc in the control pressure chamber 102 , and the spool 109 makes the bleed passage 106 in a fully opened state by a spring force of the biasing spring 112 .
  • the pressure in the control pressure chamber 102 can be reduced earlier by releasing the pressure to the suction chamber 105 through the bleed passage with a large opening degree (a period of time until all the liquid refrigerant accumulated in the control pressure chamber 102 is vaporized and discharged to the suction chamber 105 is shortened), therefore, it is possible to avoid an inconvenience that a period of time until discharge capacity can be controlled is increased. Therefore, the pressure Pc in the control pressure chamber 102 is smoothly reduced by fully closing the first control valve 104 and a tilt angle of the swash plate is smoothly increased, thereby increasing the discharge capacity.
  • the spool 109 moves against the biasing spring 112 and abuts on the valve forming body 111 , and the bleed passage 106 is in a state of being largely throttled by a communicating groove 109 a formed at a tip end portion of the spool 109 . Accordingly, a refrigerant amount introduced out of the control pressure chamber 102 to the suction chamber 105 through the bleed passage 106 is largely reduced and the pressure Pc in the control pressure chamber 102 is increased and the tilt angle of the swash plate is reduced, as a result, the discharge capacity is reduced.
  • Patent Literature 1 JP-A-2002-021721
  • a bleed amount from the control pressure chamber 102 to the suction chamber 105 is adjusted by the spool 109 housed inside the spool holding concave portion 108 so as to slide, and the pressure in the intermediate region K between the first control valve 104 of the supply passage 103 and the fixed throttle 113 is allowed to act as a back pressure acting on the spool 109 , therefore, it is necessary to strictly perform management of the clearance between the inner wall of the spool holding concave portion 108 and the spool 109 for reducing a leakage amount of the refrigerant from the intermediate region K (back pressure chamber 110 ) to the suction chamber 105 adjacent to the spool holding concave portion 108 , which causes an inconvenience that the costs are increased.
  • the clearance between the inner wall of the spool holding concave portion 108 and the spool 109 is set to a minute value, the leakage of the back pressure can be effectively suppressed, however, there may occur an inconvenience that contamination and so on are easily stuck into a sliding surface between the inner wall of the spool holding concave portion 108 and the spool 109 , which may hinder movement of the spool 109 and may interfere with pressure control in the control pressure chamber 102 .
  • the present invention has been made in view of the above circumstances and a main object thereof is to provide a variable-capacity compressor capable of increasing starting performance of the compressor and eliminating a risk of the compressor becoming uncontrollable due to contamination or the like in the refrigerant.
  • a variable-capacity compressor has a compression chamber compressing working fluid, a suction chamber housing the working fluid compressed in the compression chamber, a discharge chamber housing the working fluid compressed in the compression chamber and discharged, a control pressure chamber through which a drive shaft penetrates, housing a swash plate rotating with rotation of the drive shaft, a supply passage allowing the discharge chamber to communicate with the control pressure chamber, a bleed passage constantly allowing the control pressure chamber to communicate with the suction chamber, and a control valve adjusting an opening degree of the supply passage, in which a discharge capacity is varied by adjusting a pressure in the control pressure chamber, which includes an opening passage allowing the control pressure chamber to communicate with the suction chamber, a valve housing chamber formed on the opening passage, in which the opening passage is formed by including an upstream-side opening passage allowing the control pressure chamber to communicate with the valve housing chamber, and a downstream-side opening passage provided so as to open to one end of the housing chamber in an axial direction and allowing the valve housing
  • one end of the housing chamber in the axial direction indicates one terminal end of the housing chamber when an operation direction of the valve body is the axial direction
  • an end surface on one end side of the valve body in the axial direction indicates an end surface of one end portion in the operation direction of the valve body.
  • control valve allows the supply passage to be in the fully opened state, however, the valve body housed in the valve housing chamber is biased by the biasing means to make the downstream-side opening passage in the opened state as pressures acting before and after the valve body is balanced.
  • the pressure in the suction chamber begins to reduce to be lower than the pressure in the control pressure chamber with operation at the minimum capacity in the beginning of starting the compressor.
  • the supply passage is closed by the control valve, therefore, the pressure is not introduced to the control pressure chamber and the housing chamber.
  • the evaporated refrigerant in the control pressure chamber is discharged to the suction chamber through the bleed passage, which flows into the valve housing chamber through the upstream-side opening passage and is discharged from the valve housing chamber to the suction chamber through the downstream-side opening passage.
  • the refrigerant in the control pressure chamber can be immediately released to the suction chamber through two systems of the bleed passage and the opening passage, and a period of time until all the liquid refrigerant accumulated in the control pressure chamber is evaporated and discharged to the suction chamber can be shortened.
  • the pressure introduction passage is a passage branching from the downstream of the control valve in the supply passage, therefore, even when the refrigerant flowing into the valve housing chamber through the pressure introduction passage flows back to the control pressure chamber through the upstream-side opening passage, sum totals of a refrigerant amount flowing into the control pressure chamber via the supply passage and a refrigerant amount flowing into the control pressure chamber via the opening passage are approximately the same, which is not an obstacle for the control of discharge capacity.
  • the pressure introduction passage branches from the downstream side of the control valve in the supply passage and is connected to a region in the valve housing chamber, which is on the opposite side of the downstream-side opening passage with respect to the valve body housed in the valve housing chamber, therefore, a pressure with less pulsation on the downstream side of the control valve can be given in a direction of blocking the downstream opening passage by the valve body, and the valve body inside the valve housing chamber can be positively operated as compared with a structure where the valve body inside the valve housing chamber is opened and closed based on a pressure in the discharge chamber with many pulsations.
  • the opening of the downstream-side opening passage allowing the valve housing chamber to communicate with the suction chamber is opened/closed by the end surface on one end in the axial direction of the valve body housed in the valve housing chamber, therefore, it is not necessary to form the valve body housed in the valve housing chamber by the spool valve, and it is also not necessary to strictly manage a clearance between the valve body and the valve housing chamber.
  • a boosting means may be provided on the downstream side of the place where the pressure introduction passage branches on the supply passage.
  • the pressure on the upstream side of the boosting means can be set to be higher than the pressure in the control pressure chamber, therefore, it is possible to give a higher pressure to the valve body housed in the valve housing chamber, and more stable operation can be obtained.
  • a first check valve allowing only a flow from the upstream side to the downstream side of the supply passage is used as the boosting means, thereby adjusting a pressure difference before and after the check valve to a prescribed value by a spring force of the check valve regardless of the amount of the refrigerant flowing through the supply passage.
  • the valve body is formed by including a large-diameter portion moving along an inner peripheral surface of the valve housing chamber and a small diameter portion formed to have a smaller diameter than a diameter of the large diameter portion and opening/closing the downstream-side opening passage, and that a portion where the pressure introduction passage is connected to the valve housing chamber is positioned in a region on the opposite side of the downstream-side opening passage with respect to the large diameter portion in a state where the valve body is the most distant from the downstream-side opening passage.
  • a pressure of the refrigerant introduced into the valve housing chamber through the pressure introduction passage can be reduced at the time of passing through a clearance between a peripheral surface of the large diameter portion and an inner wall of the valve housing chamber, and a strong pressing force can be given to the small diameter portion of the valve body by a pressure acting on the large diameter portion.
  • a portion where the upstream-side opening passage is connected to the valve housing chamber is positioned closer to the downstream-side opening passage side than the large-diameter portion is in a state where the valve body is the closest to the downstream-side opening passage.
  • the pressure of the refrigerant in the control pressure chamber flowing into the valve housing chamber through the opening passage can be positively given to the downstream side of the large diameter portion (the end surface on the side where the small diameter portion is provided), and the opening passage is not blocked by the peripheral surface of the large diameter portion, therefore, it is possible to avoid increase of a passage resistance in the opening passage regardless of the position of the valve body.
  • a second check valve allowing only a flow of fluid from the control pressure chamber to the valve housing chamber is provided on the upstream-side opening passage.
  • variable-capacity compressor in which the pressure in the control pressure chamber is adjusted through the supply passage allowing the discharge chamber to communicate with the control pressure chamber to adjust the opening degree by the control valve and the bleed passage allowing the control pressure chamber to communicate with the suction chamber, the valve housing chamber connecting to the upstream-side opening passage communicating with the control pressure chamber and the downstream-side opening passage communicating with the suction chamber is provided, and the valve body opening/closing the downstream-side opening passage and biased in the direction of opening the downstream-side opening passage by the biasing means is housed in the valve housing chamber.
  • the pressure introduction passage communicating with the portion on the downstream side of the control valve in the supply passage is connected to the valve housing chamber, thereby making the pressure introduced to the valve housing chamber to act on the valve body in the direction of blocking the downstream-side opening passage.
  • the check valve allowing only the flow of fluid from the control pressure chamber to the valve housing chamber is provided on the upstream-side opening passage.
  • the valve body housed inside the valve housing chamber maintains the opened state of the downstream-side opening passage by the biasing means, therefore, the vaporized refrigerant in the control pressure chamber can be smoothly discharged to the suction chamber through the bleed passage and the opening passage, which can increase starting performance of the compressor.
  • the control valve When the pressure in the discharge chamber is increased, the control valve is opened and the high-pressure refrigerant is supplied to the valve housing chamber from the supply passage through the pressure introduction passage, and a difference between the pressure introduced into the valve housing chamber and the pressure in the suction chamber exceeds a biasing force of the biasing means, the valve body moves in the direction of blocking the downstream-side opening passage to block the opening of the downstream-side opening passage by the end surface on one end of the valve body in the axial direction.
  • the refrigerant flowing into the valve housing chamber through the pressure introduction passage does not flow into the suction chamber regardless of the clearance between the valve body and the valve housing chamber, and an inconvenience that an internal circulating refrigerant is increased and performance is reduced can be eliminated.
  • valve body for opening/closing the opening passages As the valve body for opening/closing the opening passages is opened/closed based on the pressure on the downstream side of the control valve as described above, the valve body inside the valve housing chamber can be positively operated as compared with a case where the valve body inside the valve housing chamber is opened/closed based on the pressure in the discharge chamber with many pulsations in the compressor.
  • valve body it is not necessary to use the spool valve for the valve body, therefore, it is possible to eliminate the risk of the valve body becoming uncontrollable due to contamination or the like in the refrigerant.
  • FIG. 1 is a cross-sectional view showing a compressor according to the present invention, which is a view showing a state of a beginning of starting the compressor.
  • FIG. 2 is a cross-sectional view showing the compressor according to the present invention, which is a view showing a state at the time of full stroke.
  • FIG. 3 is a cross-sectional view showing the compressor according to the present invention, which is a view showing a state at the time of controlling a discharge capacity in an intermediate stroke.
  • FIG. 4 shows structure diagrams of an opened-state adjustment mechanism for adjusting the opened state in opening passages, in which FIG. 4A is a view showing a state of beginning of starting the compressor and FIG. 4B is a view showing a state during operation of the compressor.
  • FIG. 5 is a comparison table in which opened/closed states of respective valves and strokes of pistons are summarized according to operation states.
  • FIG. 6 is a view showing a structure proposed in related art for a variable-capacity compressor.
  • a clutchless-type variable-capacity compressor that is belt-driven by a power source such as an engine.
  • the variable-capacity compressor includes a cylinder block 1 , a rear head 3 assembled to a rear side (right side in the drawing) of the cylinder block 1 through a valve plate 2 and a front head 5 assembled so as to block a front side (left side in the drawing) of the cylinder block 1 to demarcate a control pressure chamber 4 , and these front head 5 , the cylinder block 1 , the valve plate 2 and the rear head 3 are fastened in an axial direction by a fastening bolt 6 to form a housing of the compressor.
  • One end side of the drive shaft 7 is sealed with good airtightness between the drive shaft 7 and the front head 5 through a sealing member 11 provided between the drive shaft 7 and the front head 5 and supported by a radial bearing 12 so as to rotate freely.
  • the other end of the drive shaft 7 is supported by a radial bearing 14 housed in a housing hole 13 formed at approximately the center of the cylinder block 1 so as to rotate freely.
  • the housing hole 13 in which the radial bearing 14 is housed and plural cylinder bores 15 arranged at equal intervals on a circumference around the housing hole 13 are formed, and single-head pistons 16 are inserted into respective cylinder bores 15 so as to reciprocate.
  • a thrust flange 17 rotating together with the drive shaft 7 is provided securely to the drive shaft 7 in the control pressure chamber 4 .
  • the thrust flange 17 is supported so as to rotate freely with respect to an inner surface of the front head 5 through a thrust bearing 18 , and a swash plate 20 is connected to thrust flange 17 through a link member 19 .
  • the swash plate 20 is provided so as to move in a tilting manner around a hinge ball 21 provided on the drive shaft 7 so as to slide, rotating together in synchronization with rotation of the thrust flange 17 through the link member 19 . Then, engaging portions 16 a of the single-head pistons 16 are captively held to a peripheral edge portion of the swash plate 20 through pairs of shoes 22 .
  • suction holes 31 and discharge holes 32 are formed so as to correspond to respective cylinder bores 15 .
  • a suction chamber 33 housing a working fluid to be compressed in the compression chambers 23 and a discharge chamber 34 housing the working fluid compressed and discharged in the compression chambers 23 are demarcated.
  • the suction chamber 33 is formed in the central portion of the rear head 3 , communicating with a not-shown suction port connected to an exit side of an evaporator and is capable of communicating with the compression chambers 23 through the suction holes 31 opened and closed by not-shown suction valves.
  • the discharge chamber 34 is formed in a periphery of the suction chamber 33 which is capable of communicating with the compression chambers 23 through the discharge holes 32 opened and closed by not-shown discharge valves and communicating with a discharge space 37 formed in a peripheral wall portion of the cylinder block 1 through passages 2 a and 1 a formed in the valve plate 2 and the cylinder block 1 .
  • the discharge space 37 is demarcated by the cylinder block 1 and a cover 38 attached to the cylinder block 1 .
  • a discharge port 39 communicating with an inlet side of a condenser is formed in the cover 38 , and a discharge check valve 36 for preventing backflow of a refrigerant from the condenser into the discharge space 37 is provided.
  • a discharge capacity of the compressor is determined by strokes of the pistons 16 , and the strokes are determined by a tilt angle of the swash plate 20 with respect to a surface perpendicular to the drive shaft 7 .
  • the tilt angle of the swash plate 20 is balanced at an angle in which a sum total of a moment derived from a differential pressure between pressures of the compression chambers 23 (pressures inside the cylinder bores) acting on respective pistons 16 and a pressure in the control pressure chamber 4 , a moment derived from an inertia force of the swash plate or the pistons and a moment derived from a biasing force of a destroke spring 24 that biases the hinge ball 21 becomes “0 (zero)”. Accordingly, the piston strokes are determined and the discharge capacity is determined.
  • a supply passage 40 allowing the discharge chamber 34 to communicate with the control pressure chamber 4 is formed by passages 1 b, 2 b and 3 b formed over the cylinder block 1 , the valve plate 2 and the rear head 3 , and a bleed passage 41 allowing the control pressure chamber 4 to communicate with the suction chamber 33 is formed through the housing hole 13 formed in the cylinder block 1 , a passage 1 c formed continuously from the housing hole 13 , an orifice hole 2 c formed in the valve plate 2 communication with the passage 1 c, a passage 7 c formed in the drive shaft 7 , the clearance of the radial bearing 14 and the like.
  • a pressure control valve 42 is provided, and a flow rate of a refrigrant flowing into the control pressure chamber 4 from the discharge chamber 34 through the supply passage 40 is adjusted by the pressure control valve 42 to thereby control the pressure in the control pressure chamber 4 .
  • the pressure control valve 42 is inserted into a mounting hole 43 formed in the rear head 3 , which adjusts an opening degree of the supply passage 40 so that a suction pressure becomes a target value to thereby control the pressure in the control pressure chamber as well as fully opens the supply passage 40 by stopping electrical conduction and minimizes the discharge capacity by increasing the pressure in the control pressure chamber 4 .
  • the supply passage 40 is closed by maximizing the conductive amount (duty ratio is 100%), pressure supply to the control pressure chamber is stopped or other operations are performed.
  • an opening passage 50 allowing the control pressure chamber 4 to communicate with the suction chamber 33 is provided.
  • One end of the opening passage 50 is connected to the passage 1 c (portion on the upstream side of the orifice hole 2 c of the bleed passage 41 ) allowing the housing hole 13 formed in the cylinder block 1 to communicate with the orifice hole 2 c, the other end of which is connected to the suction chamber 33 through the valve plate 2 .
  • control pressure chamber 4 includes not only a space housing the drive shaft and the swash plate but also a space where a pressure of the space housing the drive shaft and the swash plate is directly reflected, and the passage 1 c allowing the housing hole 13 formed in the cylinder block 1 to communicate with the orifice hole 2 c is also part of the control pressure chamber 4 .
  • the opening passage 50 is provided with an opened-state adjustment mechanism for automatically adjusting the opened state of the passage also shown as FIG. 4 .
  • the opened-state adjustment mechanism is formed by a valve housing chamber 51 formed on the opening passage 50 , a valve body 52 provided inside the valve housing chamber 51 and a spring 53 pressing the valve body 52 , having a structure in which a downstream-side opening passage 50 b is opened and closed by the valve body 52 when a portion allowing the control pressure chamber 4 to communicate with the valve housing chamber 51 in the opening passage 50 is an upstream-side opening passage 50 a and a portion allowing the valve housing chamber 51 in the opening passage 50 to communicate with the suction chamber 33 is the downstream-side opening passage 50 b.
  • the valve housing chamber 51 is formed in a cylindrical shape, and the downstream-side opening passage 50 b opens at an end portion on one end side of the valve housing chamber 51 in the axial direction, and an opening 50 b - 1 of the downstream-side opening passage 50 b is opened and closed by an end surface 52 b - 1 on one end side of the valve body 52 in the axial direction (an end surface of a later-described first small diameter portion 52 b ).
  • the valve body 52 is biased in a direction of opening the downstream-side opening passage 50 b by the spring 53 (biasing means).
  • valve housing chamber 51 is configured by blocking a cylindrical bottomed hole formed in the cylinder block 1 by the valve plate 2 , and the downstream-side opening passage 50 b is configure by a through hole having a diameter smaller than a diameter of the valve housing chamber 51 formed on the valve plate 2 .
  • a pressure introduction passage 54 branching on the downstream side of the pressure control valve 42 of the supply passage 40 is connected to the valve housing chamber 51 (the valve housing chamber 51 communicates with the downstream side of the pressure control valve 42 of the supply passage 40 through the pressure introduction passage 54 ).
  • the pressure introduction passage 54 is connected close to an end portion on the opposite side of an end portion where the downstream-side opening passage 50 b of the valve housing chamber 51 is connected, and the upstream-side opening passage 50 a is connected to close to an end portion where the downstream-side opening passage 50 b of the valve housing chamber 51 is connected.
  • the valve body 52 housed in the valve housing chamber 51 has a shape in which a suitable throttle is formed between a portion where the pressure introduction passage 54 opens in the valve housing chamber 51 and a portion where the upstream-side opening passage 50 a opens in a state in which the downstream-side opening passage 50 b is blocked.
  • the valve body 52 is configured by including a large diameter portion 52 a moving along an inner peripheral surface in a state where a prescribed clearance is secured between the valve body 52 and the inner peripheral surface of the valve housing chamber 51 , the first small diameter portion 52 b formed continuously from the large diameter portion 52 a to have a smaller diameter than a diameter of the large diameter portion 52 a and opening/closing the downstream-side opening passage 50 b by an end surface thereof and a second small diameter portion 52 c formed continuously from the large diameter portion 52 a on the opposite side of the first diameter portion to have a smaller diameter than the diameter of the large diameter portion 52 a.
  • a portion where the pressure introduction passage 54 is connected is a position where a pressure introduced through the pressure introduction passage 54 acts on the valve body 52 in a direction of blocking the downstream-side opening passage 50 b, which is a portion to be an opposite side of the downstream-side opening passage 50 b (first small diameter portion 52 b ) with respect to the large diameter portion 52 a in a state where the valve body 52 is positioned at the most distant position from the downstream-side opening passage 50 b.
  • valve housing chamber 51 is configured so that the pressure introduction passage 54 is connected to an peripheral surface of the valve housing chamber 51 facing a peripheral surface of the second small diameter portion 52 c of the valve body 52 in the state where the valve body 52 is positioned at the most distant position from the downstream-side opening passage 50 b in the valve housing chamber 51 .
  • a portion where the upstream-side opening passage 50 a is connected in the valve housing chamber 51 is a region which is on the same side as the downstream-side opening passage 50 b (the first small diameter portion 52 b ) with respect to the large diameter portion 52 a in a state where the valve body 52 is closest to the downstream-side opening passage 50 b (in the state where the valve body 52 blocks the downstream-side opening passage 50 b ).
  • valve housing chamber 51 is configured so that the upstream-side opening passage 50 a is connected to an peripheral surface of the valve housing chamber 51 facing a peripheral surface of the first small diameter portion 52 b of the valve body 52 in the state where the valve body 52 is positioned at the closest position to the downstream-side opening passage 50 b in the valve housing chamber 51 .
  • a first check valve 60 as a boosting means is provided on the downstream side of a place where the pressure introduction passage 54 branches in the supply passage 40 .
  • the first check valve 60 allows only a flow from the upstream side to the downstream side of the supply passage 40 , housing a ball-shaped valve body 60 b in a valve-body housing portion 60 a provided on the supply passage 40 to allow the ball-shaped valve body 60 b to be seated on a seating surface 60 c provided on the upstream side of the valve body housing portion 60 a from the downstream side and to bias the ball-shaped valve body 60 b toward the seating surface 60 c from the downstream side by a spring 60 d so as to have a prescribed valve-opening pressure.
  • the upstream-side opening passage 50 a is provided with a second check valve 70 allowing only a flow from the control pressure chamber 4 (the passage 1 c formed in the cylinder block 1 ) to the valve housing chamber 51 .
  • the second check valve 70 houses a ball-shaped valve body 70 b in a valve-body housing portion 70 a provided on the upstream-side opening passage 50 a to allow the ball-shaped valve body 70 b to be seated on a seating surface 70 c provided on the control pressure chamber side of the valve body housing portion 70 a from the valve housing chamber side and to open/close the upstream-side opening passage 50 due to a pressure difference between the control pressure chamber 4 and the valve housing chamber 51 .
  • first check valve 60 the ball-shaped valve bodies are used as the check valves (first check valve 60 , second check valve 70 ) provided on the upstream-side opening passage 50 a and the supply passage 40 is shown, however, the present invention is not limited to this.
  • the pressure Pd in the discharge chamber 34 , the pressure Pc in the control pressure chamber 4 and the pressure Ps in the suction chamber 33 are approximately equivalent in a state where the compressor is stopped for a long period of time (while the engine is stopped), and the liquefied refrigerant stagnates in the control pressure chamber 4 .
  • the pressure control valve 42 is in the fully opened state as the electrical conduction is stopped, the pressure (control valve downstream pressure Pk) in the intermediate region K of the bleed passage 41 (region between the pressure control valve 42 and the first check valve 60 in the supply passage 41 ) is also approximately equivalent to the pressure Ps of the suction chamber 33 .
  • the swash plate 20 is biased by the biasing force of the destroke spring 24 so that the tilt angle with respect to the surface perpendicular to the drive shaft 7 is the smallest. Also as shown in “at the time of engine stop” of FIG. 5 , the first check valve 60 is in the closed state by the biasing force of the spring 60 d, the valve body 52 is in the opened state by the biasing force of the spring 53 , the second check valve 70 is in the opened state and the discharge check valve 36 is in the closed state.
  • the pressure in the intermediate region K (control valve downstream pressure Pk) between the pressure control valve 42 and the boosting means (the first check valve 60 ) of the supply passage 40 is approximately equivalent to the pressure Ps in the suction chamber 33 , which is lower than the pressure Pc in the control pressure chamber 4 .
  • a difference between the pressure on the downstream side of the pressure control valve 42 (control valve downstream pressure Ps) and the pressure (Ps) of the suction chamber 33 is small, therefore, the valve 52 is maintained in a position where the downstream-side opening passage 50 b is opened by the biasing force of the spring 53 as shown in “beginning of starting (when the liquid refrigerant stagnates) in FIG. 4A and FIG.
  • the pressure Pc in the control pressure chamber 4 is increased to be higher than the control valve downstream pressure Pk, therefore, the first check valve 60 forming the boosting means is in the closed state (the ball-shaped valve body 60 b abuts on the seating surface 60 c provided on the supply passage 40 ), which prevents the refrigerant in the control pressure chamber 4 from flowing back to the valve housing chamber 51 through the pressure introduction passage 54 .
  • the pressure Pc in the control pressure chamber 4 is higher than the pressure Ps in the suction chamber 33 , therefore, the second check valve 70 is in the opened state (the ball-shaped valve body 70 b is separated from seating surface 70 c provided on the upstream-side opening passage 50 a ), the vaporized refrigerant in the control pressure chamber 4 flows to the valve housing chamber 51 through the upstream-side opening passage 50 a and flows out to the suction chamber 33 from the valve housing chamber 51 .
  • the refrigerant in the control pressure chamber 4 can be immediately released to the suction chamber 33 through two systems of the bleed passage 41 and the opening passage 50 , which reduces the pressure in the control pressure chamber 4 earlier (a period of time until all the liquid refrigerant accumulated in the control pressure chamber is evaporated and discharged to the suction chamber is shortened to thereby avoid an inconvenience that a period of time until discharge capacity control can be performed is extended), as a result, it is possible to increase the tilt angle of the swash plate 20 smoothly and to increase the discharge capacity ( FIG. 2 ).
  • the conduction amount of the pressure control valve 42 is adjusted and the supply passage 40 is opened (the pressure control valve 42 is opened), and a high-pressure gas in the discharge chamber 34 is supplied to the control pressure chamber 4 through the supply passage 40 .
  • the boosting means (first check valve 60 ) is provided in the downstream of the control valve of the supply passage 40 , the control valve downstream pressure Pk can be smoothly increased by utilizing a passage resistance generated when the refrigerant passes through the boosting means, thereby giving a pressure higher than the pressure Pc in the control chamber 4 to the valve body 52 housed in the valve housing chamber 51 .
  • the boosting means is configured by the first check valve 60 having a prescribed valve-opening pressure as described above, thereby generating a prescribed pressure difference before and after the boosting means regardless of the amount of the refrigerant gas passing through the supply passage 40 .
  • valve body 52 moves in a direction of blocking the downstream-side opening passage 50 b against the spring force of the spring 53 and makes the downstream-side opening passage 50 b in the closed state as shown in “at the time of an intermediate stroke (discharge capacity control operation)” in FIG. 4B and FIG. 5 .
  • the refrigerant flowing into the valve housing chamber 51 through the pressure introduction passage 54 passes through a clearance between an inner wall of the valve housing chamber 51 and the large diameter portion 52 a of the valve 52 and flows into the control pressure chamber 4 through the upstream-side opening passage 50 a, however, the second check valve 70 allowing only the flow of fluid from the control pressure chamber 4 to the valve housing chamber 51 is provided in the upstream-side opening passage 50 a, therefore, the second check valve 70 is in the closed state and prevents the flow of the refrigerant to the control pressure chamber 4 through the upstream-side opening passage 50 a.
  • the refrigerant in the control pressure chamber 4 is discharged to the suction chamber 33 only through the related-art bleed passage 41 , and the high pressure gas is supplied to the control pressure chamber 4 through the supply passage 40 in a state where the refrigerant amount introduced out of the control pressure chamber 4 to the suction chamber 33 is drastically reduced, therefore, the pressure Pc in the control pressure chamber 4 is smoothly increased and the tilt angle of the swash plate 20 is smoothly reduced to thereby reduce the discharge amount ( FIG. 3 ).
  • the pressure introduction passage 54 is connected to a portion of the valve housing chamber 51 on the opposite side of the downstream-side opening passage 50 b (the first small diameter portion 52 b ) with respect to the large diameter portion 52 a in the state where the valve body 52 is the most distant from the downstream-side opening passage 50 b, therefore, a pressure of the refrigerant introduced into the valve housing chamber 51 through the pressure introduction passage 54 can be reduced when passing through a clearance between a peripheral surface of the large diameter portion 52 a and the inner wall of the valve housing chamber 51 , thereby generating a difference between a pressure acting on one end side of the valve body 52 in the axial direction and a pressure acting on the other end side in the axial direction and giving a pressing force in the direction of blocking the downstream-side opening passage 50 b against the biasing force of the spring 53 .
  • the upstream-side opening passage 50 a is connected to a portion to be closer to the downstream-side opening passage than the large diameter portion 52 a is in the state where the valve body 52 is the closest to the downstream-side opening passage 50 b (state where the downstream-side opening passage 50 b is blocked by the valve body 52 ), therefore, the refrigerant pressure Pc in the control pressure chamber 4 flowing into the valve housing chamber 51 through the upstream-side opening passage 50 a can be positively given to the downstream side in the large diameter portion (end surface on the side where the first small diameter portion 52 b is provided), and the opening passage 50 is not blocked by the peripheral surface of the large diameter portion 52 a, therefore, it is possible to avoid the increase in the passage resistance of the opening passage 50 regardless of the position of the valve body 52 .
  • the pressure control valve 42 is fully opened and the high-pressure refrigerant is supplied from the discharge chamber 34 to the control pressure chamber 4 through the supply passage 40 to thereby minimize piston strokes for minimizing the discharge capacity of the compressor as shown in “at the time of idling (clutchless off operation)” in FIG. 5 .
  • the high-pressure gas is supplied from the supply passage 40 to the valve housing chamber 51 through the pressure introduction passage 54 , therefore, the valve body 52 is immediately closed, the pressure Pc in the control pressure chamber 4 is smoothly increased, the tilt angle of the swash plate 20 is smoothly reduced and the discharge capacity is reduced.
  • valve body inside the valve housing chamber 51 is controlled to be opened and closed based on the pressure on the downstream side (control valve downstream pressure Pk) of the pressure control valve 42 in the supply passage 40 , therefore, the valve body inside the valve housing chamber can be positively operated as compared with a case where the valve body inside the valve housing chamber is controlled to be opened and closed based on a pressure in the discharge chamber 34 with many pulsations.
  • the flow of the refrigerant from the valve housing chamber 51 to the control pressure chamber 4 can be interrupted by the second check valve 70 in the case where the downstream-side opening passage 50 b is in the closed state by the valve body 52 even when the valve body 52 does not have the structure like spool valve, therefore, the inconvenient that the amount of the refrigerant supplied to the control pressure chamber is reduced through the supply passage does not occur and lubrication for slicing components inside the control pressure chamber can be secured.
  • valve body 52 it is possible to avoid using the spool valve as the valve body 52 in the above structure, therefore, it is not necessary to strictly manage the clearance between the valve body 52 and the valve housing chamber 51 , and contamination or the like in the refrigerant does not affect movement of the valve body.
  • the conduction amount to the pressure control valve 42 is increased and the supply passage 40 is closed, then, the pressure is not supplied from the discharge chamber 34 to the control pressure chamber 4 through the pressure control valve 42 .
  • the pressure in the intermediate region K (control valve downstream pressure Pk) of the supply passage 40 is lower than the pressure Pc in the control pressure chamber 4 , therefore, the ball-shaped valve body 60 b in the first check valve 60 abuts on the seating surface 60 c and the supply passage 40 is blocked.
  • the portion of the pressure introduction passage 54 that opens to the valve housing chamber 51 has a structure in which the control valve downstream pressure Pk introduced to the valve housing chamber 51 acts on the valve body 52 in the direction of blocking the downstream-side opening passage 50 b, therefore, the structure is not limited to the example shown in FIG. 4 .
  • the structure in which the first check valve 60 as the boosting means is provided on the downstream side of the place where the pressure introduction passage 54 of the supply passage 40 branches is shown, however, it is also preferable that the orifice hole substitutes for the boosting means as well as that the boosting means can be omitted.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
US15/561,672 2015-03-26 2016-03-24 Variable-capacity compressor Abandoned US20180073499A1 (en)

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JP2015-064294 2015-03-26
JP2015064294 2015-03-26
PCT/JP2016/059317 WO2016152959A1 (ja) 2015-03-26 2016-03-24 可変容量型圧縮機

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JP (1) JP6732387B2 (ja)
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EP3822485B1 (en) * 2018-07-13 2024-04-10 Eagle Industry Co., Ltd. Capacity control valve

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US6358017B1 (en) * 1999-08-31 2002-03-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve for variable displacement compressor
US20030010048A1 (en) * 2001-07-13 2003-01-16 Masakazu Murase Flow restricting structure in displacement controlling mechanism of variable displacement compressor
JP2005307882A (ja) * 2004-04-22 2005-11-04 Toyota Industries Corp 可変容量型圧縮機における容量制御機構
US20060165535A1 (en) * 2005-01-27 2006-07-27 Masaki Ota Variable displacement compressor
US20090116971A1 (en) * 2007-11-05 2009-05-07 Taro Ozeki Variable displacement compressor
US7559208B2 (en) * 2004-10-04 2009-07-14 Kabushiki Kaisha Toyota Jidoshokki Displacement control mechanism for variable displacement compressor
US20090269216A1 (en) * 2008-04-28 2009-10-29 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type compressor with displacement control mechanism
US20100104454A1 (en) * 2008-10-28 2010-04-29 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type compressor with displacement control mechanism
US20110214564A1 (en) * 2010-03-08 2011-09-08 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor
US20120247140A1 (en) * 2011-03-31 2012-10-04 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor

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JPS62119483U (ja) * 1986-01-21 1987-07-29
JP2005009422A (ja) * 2003-06-19 2005-01-13 Toyota Industries Corp 容量可変型圧縮機の容量制御機構

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Publication number Priority date Publication date Assignee Title
US6358017B1 (en) * 1999-08-31 2002-03-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Control valve for variable displacement compressor
US20030010048A1 (en) * 2001-07-13 2003-01-16 Masakazu Murase Flow restricting structure in displacement controlling mechanism of variable displacement compressor
JP2005307882A (ja) * 2004-04-22 2005-11-04 Toyota Industries Corp 可変容量型圧縮機における容量制御機構
US7559208B2 (en) * 2004-10-04 2009-07-14 Kabushiki Kaisha Toyota Jidoshokki Displacement control mechanism for variable displacement compressor
US20060165535A1 (en) * 2005-01-27 2006-07-27 Masaki Ota Variable displacement compressor
US20090116971A1 (en) * 2007-11-05 2009-05-07 Taro Ozeki Variable displacement compressor
US20090269216A1 (en) * 2008-04-28 2009-10-29 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type compressor with displacement control mechanism
US20100104454A1 (en) * 2008-10-28 2010-04-29 Kabushiki Kaisha Toyota Jidoshokki Variable displacement type compressor with displacement control mechanism
US20110214564A1 (en) * 2010-03-08 2011-09-08 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor
US20120247140A1 (en) * 2011-03-31 2012-10-04 Kabushiki Kaisha Toyota Jidoshokki Variable displacement compressor

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EP3293395A4 (en) 2019-01-23
JP6732387B2 (ja) 2020-07-29
WO2016152959A1 (ja) 2016-09-29
EP3293395A1 (en) 2018-03-14
CN107407267A (zh) 2017-11-28
JPWO2016152959A1 (ja) 2018-02-22

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