WO2019167504A1 - Compresseur à débit variable - Google Patents

Compresseur à débit variable Download PDF

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Publication number
WO2019167504A1
WO2019167504A1 PCT/JP2019/002606 JP2019002606W WO2019167504A1 WO 2019167504 A1 WO2019167504 A1 WO 2019167504A1 JP 2019002606 W JP2019002606 W JP 2019002606W WO 2019167504 A1 WO2019167504 A1 WO 2019167504A1
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WO
WIPO (PCT)
Prior art keywords
swash plate
rotor
arm
pin
drive shaft
Prior art date
Application number
PCT/JP2019/002606
Other languages
English (en)
Japanese (ja)
Inventor
石川　勉
中村　慎二
慧祐 橋場
伊藤　隆博
篤史 小澤
Original Assignee
サンデン・オートモーティブコンポーネント株式会社
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by サンデン・オートモーティブコンポーネント株式会社 filed Critical サンデン・オートモーティブコンポーネント株式会社
Priority to CN201980012657.0A priority Critical patent/CN111699317B/zh
Publication of WO2019167504A1 publication Critical patent/WO2019167504A1/fr

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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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
    • F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
    • F04B27/10—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B27/12—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having plural sets of cylinders or pistons
    • 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

Definitions

  • the present invention relates to a variable capacity compressor capable of changing a discharge capacity by changing an inclination angle of a swash plate that rotates integrally with a drive shaft.
  • variable capacity compressor for example, a variable capacity compressor described in Patent Document 1 is known.
  • the variable capacity compressor described in Patent Document 1 includes a drive shaft that is rotatably supported by a housing, a rotor that is integrated with the drive shaft and rotates with the drive shaft, and an axis of the drive shaft. And a swash plate supported by the drive shaft in a state of facing the rotor so as to be slidable in the extending direction and capable of changing an inclination angle with respect to the axis.
  • the stroke amount of the piston changes in accordance with the change in the inclination angle of the swash plate, and the discharge capacity changes.
  • the swash plate is tiltably coupled to the rotor fixed to the drive shaft via a link mechanism (hereinafter referred to as a hinge mechanism), and via the hinge mechanism.
  • the rotational force of the rotor is transmitted to the swash plate.
  • the hinge mechanism includes a first arm projecting from the rotor and a second arm projecting from the swash plate, and the rotational force of the rotor passes through the first arm and the first arm of the swash plate is rotated. Is transmitted to two arms.
  • the hinge mechanism has a function of transmitting the rotational force of the rotor to the swash plate and a function of determining a trajectory of tilting in the swash plate.
  • an object of the present invention is to provide a variable capacity compressor having a hinge mechanism that can transmit a rotational force from a rotor to a swash plate with a simple structure and can determine a trajectory of tilting of the swash plate. .
  • a variable capacity compressor is slidable in a direction in which an axis of the drive shaft extends, a drive shaft rotatably supported by a housing, a rotor integrated with the drive shaft, and A swash plate supported by the drive shaft in a state of being opposed to the rotor so as to be able to change an inclination angle with respect to an axis, a rotor arm projecting from a rotor end surface on the swash plate side of the rotor toward the swash plate, The swash plate projects from the swash plate end face of the swash plate toward the rotor, and is disposed in a cylinder bore formed in the housing, and a swash plate arm to which the rotational force of the rotor is transmitted via the rotor arm.
  • the rotor arm includes two rotor arm wall portions that are spaced apart from each other and face each other.
  • the swash plate arm is composed of two swash plate arm wall portions that are inserted between mutually opposing inner wall surfaces of the two rotor arm wall portions and are spaced apart from each other.
  • Each of the two swash plate arm wall portions has a wall surface that can be slidably contacted with the inner wall surface.
  • the variable capacity compressor includes a pin and a projecting portion. The pin is connected between one tip and the other tip of the two swash plate arm walls.
  • the projecting portion is a projecting portion projecting in a predetermined region between the two rotor arm wall portions on the rotor end surface, and is separated from the rotor end surface toward the center from the outer edge portion of the rotor. And an inclined surface with which a predetermined portion of the pin between the two swash plate arm walls abuts.
  • the rotor arm that protrudes toward the swash plate from the rotor end surface on the swash plate side of the rotor includes two rotor arm wall portions that are spaced apart from each other and face each other.
  • Two swash plate arm walls which are inserted between mutually opposing inner wall surfaces of the two rotor arm wall portions and are spaced apart from each other and are opposed to each other from the rotor end surface on the rotor side of the plate toward the rotor Consists of parts. Therefore, when the rotor rotates, one of the inner wall surfaces of the two rotor arm wall portions comes into contact with the opposite wall surface, so that the rotational force of the rotor is directly applied via the rotor arm.
  • the variable capacity compressor includes a pin connected between one tip portion and the other tip portion of the two swash plate arm wall portions, and between the two rotor arm wall portions of the rotor end face.
  • a projecting portion projecting in a predetermined region, and the projecting portion has an inclined surface that inclines away from the rotor end surface toward the center from the outer edge portion of the rotor.
  • a predetermined portion of the pin between the two swash plate arm walls abuts. Therefore, when the predetermined portion of the pin slides on the inclined surface, the inclination trajectory of the swash plate is determined.
  • the rotor arm, the swash plate arm, the pin, and the projecting portion constitute a hinge mechanism that transmits a rotational force from the rotor to the swash plate and determines a tilting trajectory of the swash plate.
  • the variable displacement compressor disclosed in Patent Document 1 as the hinge mechanism requires the first arm, the second arm, the first connection pin, the second connection pin, and the link arm.
  • the variable displacement compressor according to the side surface since only the rotor arm, the swash plate arm, the pin, and the projecting portion are required, the number of parts can be reduced as compared with the conventional one, and at least in this respect, a simple structure
  • the hinge mechanism can be provided. In this way, it is possible to provide a variable capacity compressor including a hinge mechanism that can transmit a rotational force from a rotor to a swash plate with a simple structure and can determine a trajectory of tilting of the swash plate.
  • variable capacity compressor which concerns on one Embodiment of this invention. It is sectional drawing of the principal part containing the rotor and swash plate of the said variable capacity compressor. It is sectional drawing of the said principal part which shows an example of the state which the said swash plate inclined. It is a side view of the assembly containing the drive shaft of the said variable capacity compressor, a rotor, a swash plate, and a hinge mechanism. It is the side view which looked at the said assembly from another angle. It is a perspective view of the said assembly. It is a side view for demonstrating the modification of the protrusion part of the said hinge mechanism. It is a side view for demonstrating another modification of the said protrusion part.
  • FIG. 1 is a sectional view of a so-called swash plate type variable capacity compressor 100 which is an example of a variable capacity compressor to which the present invention is applied.
  • the variable capacity compressor 100 is incorporated in a refrigerant circuit of a vehicle air conditioner system, and sucks, compresses and discharges the refrigerant.
  • a variable capacity compressor 100 includes a cylinder block 101 having a plurality of cylinder bores 101a, a front housing 102 provided at one end of the cylinder block 101 via a center gasket 102a, and a cylinder block 101.
  • a cylinder head 104 provided via a valve plate 103 at the other end.
  • the front housing 102, the center gasket 102a, the cylinder block 101, the cylinder gasket (not shown), the valve plate 103, the head gasket (not shown), the cylinder head 104, and the like are fastened by a plurality of through bolts 105, so that variable capacity compression is achieved.
  • a housing for machine 100 is formed.
  • a crank chamber H1 is formed by the cylinder block 101 and the front housing 102, and a drive shaft 110 is provided so as to traverse the crank chamber H1.
  • the drive shaft 110 is rotatably supported by the housing including the cylinder block 101, the front housing 102, the cylinder head 104, and the like.
  • One end of the drive shaft 110 extends through the boss portion 102b of the front housing 102 to the outside of the front housing 102, and is connected to a power transmission device (not shown).
  • a shaft sealing device 120 is inserted between the drive shaft 110 and the boss portion 102b, and the crank chamber H1 is kept sealed.
  • the drive shaft 110 is supported by radial bearings 121 and 122 in the radial direction, and is supported by a thrust plate 123 in the thrust direction.
  • the other end of the drive shaft 110 and the thrust plate 123 are adjusted to have a predetermined gap by an adjusting screw 124.
  • the drive shaft 110 rotates in synchronization with the power transmission device when power from an external drive source (not shown) is transmitted to the power transmission device.
  • a sleeve 130 is slidably attached to the outer peripheral surface of the drive shaft 110 at a predetermined position in the extending direction of the axis X0 in the crank chamber H1 of the drive shaft 110.
  • the sleeve 130 is attached to the drive shaft 110 so as to be capable of relative rotation around the axis X0 of the drive shaft 110 and sliding (sliding movement) in the extending direction of the axis X0 with respect to the outer peripheral surface of the drive shaft 110.
  • a rotor 111 and a swash plate 112 are arranged so as to face each other. As shown in FIGS.
  • FIG. 2 is a cross-sectional view of a main part including the rotor 111 and the swash plate 112 of the variable capacity compressor 100
  • FIG. 3 is a cross-sectional view of the main part showing an example of a state in which the swash plate 112 is inclined.
  • the rotor 111 is integrated with the drive shaft 110 between the sleeve 130 and the inner wall surface on the shaft seal device 120 side in the crank chamber H1, and rotates together with the drive shaft 110.
  • the rotor 111 is formed in a substantially disk shape, and is supported by a thrust bearing 125 fixed to the inner wall of the crank chamber H1 on the shaft seal device 120 side in the thrust direction.
  • a receiving surface 111a orthogonal to the axis X0 of the drive shaft 110 is formed on the surface of the rotor 111 on the shaft seal device 120 side, and this receiving surface 111a contacts the thrust bearing 125.
  • the swash plate 112 is slidable in the extending direction of the axis X0 of the drive shaft 110 and faces the rotor 111 so that the inclination angle ⁇ (see FIG. 3) with respect to the axis X0 can be changed.
  • the swash plate 112 has an engaging portion 112 a that houses the sleeve 130 therein and engages the sleeve 130.
  • a state in which the swash plate 112 is orthogonal to the drive shaft 110 is set as a reference for the inclination angle ⁇ , that is, 0 degrees. 112 becomes larger as it is tilted from this state.
  • the swash plate 112 includes, for example, a swash plate body 112b and a swash plate boss 112c that supports the swash plate body 112b.
  • the swash plate body 112b is formed in a disk shape having a through hole 112b1 in the center.
  • the swash plate boss 112c has a boss 112c1 that fits into the through hole 112b1 of the swash plate main body 112b.
  • the swash plate body 112b and the swash plate boss 112c are fastened to each other by a rivet 112d in a state where the boss 112c1 is fitted in the through hole 112b1.
  • the engaging portion 112a is formed on the swash plate boss portion 112c.
  • the rotational force of the rotor 111 is transmitted to the swash plate 112 via the hinge mechanism 140, and the hinge mechanism 140 includes a sliding movement in the extending direction of the axis X0 and an inclination movement with respect to the axis X0 on the swash plate 112.
  • a compound tilt trajectory is defined (the tilt of the swash plate 112 is guided).
  • the hinge mechanism 140 will be described in detail later.
  • the penetration part including the engaging part 112a through which the drive shaft 110 penetrates in the center part of the swash plate 112 (swash plate boss part 112c) is formed in a shape that allows the swash plate 112 to tilt within the range of the maximum inclination angle to the minimum inclination angle. Has been.
  • a recessed portion 112e that is wound to allow tilting of the swash plate 112 (swash plate boss portion 112c) to the maximum tilt angle is formed in the opening portion of the penetrating portion opposite to the rotor 111.
  • a maximum inclination angle restricting portion 112c2 that restricts the inclination angle displacement (tilting) of the swash plate 112 in the direction of increasing the inclination angle of the swash plate 112. Projecting toward the rotor 111 side.
  • the drive shaft 110 biases the swash plate 112 in a direction to increase the tilt angle ⁇ , and a tilt angle reducing spring 113 that biases the swash plate 112 in a direction to decrease the tilt angle ⁇ .
  • An inclination angle increasing spring 114 is mounted with the swash plate 112 interposed therebetween.
  • the inclination angle decreasing spring 113 is mounted between one end face of the sleeve 130 in the full length direction of the sleeve 130 accommodated in the engaging portion 112a of the swash plate 112 and the rotor 111.
  • 114 is mounted between the other end surface of the sleeve 130 in the entire length direction of the sleeve 130 and a spring support member 115 fixed or formed on the drive shaft 110.
  • the urging force of the inclination angle increasing spring 114 is set to be larger than the urging force of the inclination angle decreasing spring 113.
  • the swash plate 112 has the biasing force of the tilt angle decreasing spring 113 and the biasing force of the tilt angle increasing spring 114.
  • the inclination angle at which the urging force of the inclination angle decreasing spring 113 and the urging force of the inclination angle increasing spring 114 balance is set as a minimum inclination angle range in which a compression operation by a piston 126 described later is ensured. Can be set in the range of ⁇ 3 degrees.
  • a piston 126 is arranged in each cylinder bore 101a formed in the cylinder block 101.
  • the piston 126 reciprocates as the swash plate 112 rotates.
  • a pair of shoes 127 and 127 are slidably accommodated in a protrusion 126a protruding from the end of the piston 126 on the swash plate side.
  • the pair of shoes 127 and 127 are formed so as to slidably hold both end surfaces in the thickness direction of the outer edge portion of the swash plate 112 (specifically, the swash plate main body portion 112b). Connect between the two.
  • the rotational movement of the swash plate 112 can be converted into the reciprocating movement of the piston 126 via a pair of shoes 127 and 127.
  • the piston 126 reciprocates with the rotational movement of the swash plate 112.
  • a suction chamber H2 is formed at the center thereof, and a discharge chamber H3 is formed at a position surrounding the suction chamber H2 in an annular shape.
  • the suction chamber H2 communicates with each cylinder bore 101a via a suction hole 103a formed in the valve plate 103 and a suction valve (not shown).
  • the discharge chamber H3 communicates with the cylinder bore 101a through a discharge hole 103b formed in the valve plate 103 and a discharge valve (not shown).
  • the cylinder head 104 is formed with a suction passage 104b having a suction port 104a.
  • the suction port 104a is connected to the low-pressure side refrigerant circuit (suction side refrigerant circuit) of the vehicle air conditioner system, and the suction passage 104b extends linearly from the outer periphery of the cylinder head 104 so as to cross a part above the discharge chamber H3. Established. As a result, the refrigerant gas flows into the suction chamber H2 from the suction passage 104b.
  • a muffler 150 that reduces noise and vibration due to refrigerant pulsation is provided on the side of the cylinder block 101.
  • the muffler 150 is formed by fastening the lid member 106 with a bolt via a seal member (not shown) to a muffler forming wall 101b protruding from the side wall of the cylinder block 101.
  • a check valve 200 that suppresses the backflow of the refrigerant gas from the discharge side refrigerant circuit to the discharge chamber H3 is disposed.
  • the check valve 200 is disposed at a connection portion between the communication path 150a that is formed across the cylinder head 104, the valve plate 103, and the cylinder block 101 and communicates with the discharge chamber H3 and the muffler space H4.
  • the check valve 200 operates in response to a pressure difference between the communication path 150a (upstream side) and the muffler space H4 (downstream side), and shuts off the communication path 150a when the pressure difference is smaller than a predetermined value.
  • the communication path 150a is opened. Therefore, the discharge chamber H3 is connected to the discharge side of the vehicle air conditioner system via the discharge passage formed by the communication passage 150a, the check valve 200, the muffler space H4, and the discharge port 106a formed in the lid member 106.
  • the cylinder head 104 is further provided with a capacity control valve 300.
  • the capacity control valve 300 adjusts the opening degree (flow passage cross-sectional area) of the supply passage 145 connecting between the discharge chamber H3 and the crank chamber H1, and thereby the refrigerant in the discharge chamber H3 flows into the crank chamber H1.
  • the supply amount is controlled.
  • the refrigerant in the crank chamber H1 is configured to flow to the suction chamber H2 via the communication passage 101c formed in the cylinder head 104, the space 101d, and the orifice 103c formed in the valve plate 103.
  • the discharge capacity of the variable capacity compressor 100 can be changed by decreasing or increasing the capacity. That is, the variable displacement compressor 100 is configured such that the stroke amount of the piston 126 changes according to the pressure in the crank chamber H1, and the discharge capacity changes.
  • the crank chamber H1 changes the discharge capacity by changing the stroke amount of the piston 126 according to the internal pressure.
  • the pressure difference before and after each piston 126 in other words, the pressure difference between the compression chamber in the cylinder bore 101a sandwiching the piston 126 and the crank chamber H1 is used.
  • the inclination angle of the swash plate 112 can be changed. As a result, the stroke amount of the piston 126 changes and the discharge capacity of the variable capacity compressor 100 changes.
  • the capacity control valve 300 basically opens the supply passage 145 so that the pressure in the suction chamber H2 becomes a pressure set by the signal based on the air conditioning setting (chamber interior setting temperature), the external environment, and the like. Configured to adjust the degree.
  • FIGS. 4 and 5 are side views of the assembly including the drive shaft 110, the rotor 111, and the swash plate 112, and FIG. 5 is a side view of the assembly as viewed from the direction of arrow A shown in FIG.
  • FIG. 6 is a perspective view of the assembly.
  • the drive shaft 110 is clockwise around the axis X0 when viewed toward the end face of the drive shaft 110 on the power transmission device side (external power input side, lower side in the figure).
  • the rotation is assumed to be in the rotation direction R (see the direction indicated by the thick arrow in FIGS. 4 to 6), and will be described below.
  • the hinge mechanism 140 transmits the rotational force of the rotor 111 to the swash plate 112 and determines the tilting trajectory of the swash plate 112.
  • the rotor arm 141, the swash plate arm 142, the pin 143, and the projecting portion 144 are examples of the projecting portion 144.
  • the rotor arm 141 is formed so as to protrude from the rotor end surface on the swash plate side of the rotor 111 toward the swash plate 112.
  • the rotor end surface on the swash plate side of the rotor 111 is divided into a semicircular region where the swash plate 112 approaches and a semicircular region where the swash plate 112 moves away.
  • the rotor arm 141 protrudes in the semicircular region (the region on the left side of the axis X0 in FIGS. 2 to 4) of the rotor end surface where the swash plate 112 is separated. As shown in FIGS.
  • the rotor arm 141 includes two rotor arm wall portions 141 a and 141 b that are spaced apart from each other and face each other. Specifically, the rotor arm wall portions 141a and 141b are opposed to each other at a distance from each other in the front-rear direction in the rotational direction R. Inner wall surfaces 141a1 and 141b1 facing each other in the two rotor arm wall portions 141a and 141b extend substantially parallel to each other. In FIG.
  • the inner wall surface 141a1 of the left rotor arm wall portion 141a is referred to as a left inner wall surface 141a
  • the inner wall surface 141b1 of the right rotor arm wall portion 141b is referred to as a right inner wall surface 141b1, as appropriate.
  • a virtual plane P extending along the axis X0 of the drive shaft 110 is located between the left inner wall surface 141a1 and the right inner wall surface 141b1.
  • the left inner wall surface 141a1 and the right inner wall surface 141b1 are extended so that, for example, the virtual plane P is located between the left inner wall surface 141a1 and the left inner wall surface 141a1 (substantially intermediate in the drawing).
  • the swash plate arm 142 projects from the swash plate end surface of the swash plate 112 toward the rotor 111.
  • the rotational force of the rotor 111 is transmitted to the swash plate arm 142 via the rotor arm 141.
  • the swash plate end surface on the rotor side of the swash plate 112 is divided into a semicircular region approaching the rotor 111 and a semicircular region moving away from the rotor 111.
  • the swash plate arm 142 projects from the semicircular region (the region on the left side of the axis X0 in FIGS. 2 to 4) of the end surface of the swash plate away from the rotor 111.
  • the swash plate arm 142 is, for example, protruded from the semicircular region away from the rotor 111 in the swash plate boss portion 112c. As shown in FIGS.
  • the swash plate arm 142 is formed between the inner wall surfaces 141a1 and 141b1 facing each other in the two rotor arm walls 141a and 141b (in other words, between the left inner wall surface 141a1 and the right inner wall surface 141b1). Between).
  • the swash plate arm 142 includes two swash plate arm wall portions 142a and 142b that are spaced apart from each other and face each other.
  • the swash plate arm walls 142a and 142b are opposed to each other at a distance from the front and rear in the rotational direction R.
  • the two swash plate arm wall portions 142a and 142b have wall surfaces 142a1 and 142b1 that can slide in contact with the inner wall surfaces 141a1 and 141b1 of the rotor arm 141, respectively.
  • holes 142a3 and 142b3 into which pins 143 can be inserted are formed at the tip ends 142a2 and 142b2 of the two swash plate arm walls 142a and 142b, respectively.
  • the wall surface 142a1 facing the left inner wall surface 141a1 will be referred to as the left outer wall surface 142a1
  • the wall surface 142b1 facing the right inner wall surface 141b1 will be referred to as the right outer wall surface 142b1, as appropriate.
  • the total width (distance between the left outer wall surface 142a1 and the right outer wall surface 142b1) of the two swash plate arm wall portions 142a and 142b in the swash plate arm 142 in the separating direction is the two rotor arm wall portions 141a in the rotor arm 141. , 141b (the distance between the left inner wall surface 141a1 and the right inner wall surface 141b1). That is, during insertion, the swash plate arm 142 has a predetermined distance between the left outer wall surface 142a1 and the left inner wall surface 141a1 or between the right outer wall surface 142b1 and the right inner wall surface 141b1.
  • the full width is set.
  • the pin 143 is a member connected between one tip portion 142a2 and the other tip portion 142b2 of the two swash plate arm wall portions 142a and 142b.
  • the pins 143 are formed in a cylindrical shape extending with the same diameter.
  • the pin 143 is supported by inserting the end portions 143a and 143b in the extending direction into holes 142a3 and 142b3 formed in the tip portions 142a2 and 142b2 of the two swash plate arm wall portions 142a and 142b, respectively.
  • each hole 142a3, 142b3 is formed with a hole diameter that allows the pin 143 to be loosely fitted (can be loosely fitted).
  • each hole 142a3, 142b3 is a through-hole penetrating in the wall thickness direction of the swash plate arm walls 142a, 142b. Therefore, since both ends 143a and 143b of the pin 143 are merely loosely fitted in the holes 142a3 and 142b3, respectively, it is necessary to devise a way to prevent the pin 143 from coming off. In the present embodiment, as shown in FIGS. 2 and 3, the pin 143 is prevented from coming off in the extending direction of the pin 143 in the entire range from the minimum inclination angle to the maximum inclination angle (full inclination state).
  • the end surfaces 143a1 and 143b1 When viewed directly facing the end surfaces 143a1 and 143b1, at least a part of the end surfaces 143a1 and 143b1 is configured to be located in a region between the two rotor arm wall portions 141a and 141b. That is, although the pin 143 is loosely fitted in the holes 142a3 and 142b3, the movement of the pin 143 in the extending direction of the pin 143 in the fully tilted state of the swash plate 112 causes the inner wall surfaces 141a1 and 141b1 of the rotor arm 141 to move. It is regulated by. Thereby, the pin 143 is prevented from coming off.
  • the protruding portion 144 protrudes in a predetermined region between the two rotor arm wall portions 141 a and 141 b on the rotor end surface on the swash plate side of the rotor 111.
  • the projecting portion 144 is inclined so as to move away from the rotor end face toward the center from the radial outer edge portion of the rotor 111, and a predetermined portion between the two swash plate arm wall portions 142a and 142b in the pin 143 is provided. It has the inclined surface 144a which contacts.
  • the projecting portion 144 has, for example, a rectangular cross section having a long side in the direction from the radially outer edge of the rotor 111 toward the center and a short side in a direction orthogonal to the long side, and the two rotor arm wall portions 141a and 141b.
  • the inclined surface 144a constitutes a protruding end surface (upper end surface) of the projecting portion 144, and has a rectangular end surface. Further, as shown in FIGS. 2 and 3, the inclined surface 144 a is extended in a range in which the outer peripheral surface of the pin 143 can come into contact with the swash plate 112 in a fully tilted state.
  • the projecting portion 144 is disposed so that the center position in the width direction (short side direction) of the inclined surface 144a is located on the virtual plane P extending along the axis X0 of the drive shaft 110. Therefore, the predetermined portion of the pin 143 that contacts the inclined surface 144a is an intermediate portion of the pin 143 between the two swash plate arm wall portions 142a and 142b.
  • the central axis of the pin 143 is orthogonal to the axis X0 of the drive shaft 110 and extends parallel to the inclined surface 144a, and the pin 143 is formed in a linearly extending columnar shape.
  • the pin 143 is assembled so that the outer peripheral surface thereof can be brought into contact with the inclined surface 144a by line contact over the entire width direction of the inclined surface 144a.
  • rotation and tilting of the swash plate 112 will be described with reference to FIGS.
  • the swash plate 112 is supported by the drive shaft 110 via the sleeve 130 and is sandwiched between the inclination angle decreasing spring 113 and the inclination angle increasing spring 114.
  • the urging force of the inclination angle increasing spring 114 is set to be larger than the urging force of the inclination angle decreasing spring 113, the swash plate 112 is mainly driven by the urging force of the inclination angle increasing spring 114.
  • the outer peripheral surface of the pin 143 assembled to the swash plate arm 142 protruding from the swash plate 112 is in contact with the inclined surface 144a.
  • the outer peripheral surface of the pin 143 contacts the end of the inclined surface 144a on the rotor outer edge side, and the maximum inclination angle restricting portion 112c2 of the swash plate 112 is the rotor. 111, so that the swash plate 112 is inclined at the maximum inclination angle.
  • the capacity control valve 300 is not energized and the supply passage 145 is fully opened.
  • the pressure in the crank chamber H1 is approximately equal to the pressure in the compression chamber in the cylinder bore 101a communicating with the suction chamber H2, for example.
  • the left inner wall surface 141a1 of the rotor arm 141 comes into contact with the left outer wall surface 142a1 of the swash plate arm 142 opposed thereto, so that the rotor 111 Is transmitted to the swash plate arm 142 (that is, the swash plate 112) via the rotor arm 141.
  • the swash plate 112 rotates with the drive shaft 110 and the rotor 111 in a state where the swash plate 112 is inclined at the maximum inclination angle and the pin 143 is in contact with the inclined surface 144a.
  • the pressure in the crank chamber H1 is increased. Get higher.
  • the swash plate 112 begins to tilt and move in the direction of decreasing the tilt angle.
  • the pin 143 slides on the inclined surface 144a toward the center side of the rotor 111 in a state of being in contact with the inclined surface 144a.
  • the swash plate 112 tilts and moves in a direction that decreases the tilt angle ⁇ with respect to the axis X0 and slides away from the rotor 111 in the extending direction of the axis X0.
  • the swash plate 112 further tilts and moves in a direction to further decrease the tilt angle ⁇ with the pin 143 in contact with the tilted surface 144a, and then the tilt angle.
  • Inclination moves to an inclination angle (> minimum inclination angle) at which the urging force of the reducing spring 113 and the urging force of the inclination angle increasing spring 114 are balanced.
  • the opening of the supply passage 145 is throttled by the capacity control valve 300, the pressure in the crank chamber H1 is reduced, and the swash plate 112 is tilted and moved in the direction of increasing the tilt angle ⁇ . Then, it slides in a direction approaching the rotor 111 in the extending direction of the axis X0.
  • the rotational force of the rotor 111 is transmitted to the swash plate 112 via the hinge mechanism 140, and the hinge mechanism 140 causes the swash plate 112 to slide in the extending direction of the axis X0 and to tilt with respect to the axis X0.
  • Complex tilt trajectories including movement are defined.
  • the left inner wall surface 141a1 which is one of the inner wall surfaces 141a1 and 141b1 of the two rotor arm wall portions 141a and 141b is added thereto.
  • the rotational force of the rotor 111 is directly transmitted to the swash plate arm 142 (that is, the swash plate 112) through the rotor arm 141 by contacting the left outer wall surface 142a1 that is the opposing wall surface. Then, the predetermined portion of the pin 143 slides on the inclined surface 144a of the projecting portion 144, whereby the inclination trajectory of the swash plate 112 is determined. That is, the hinge mechanism 140 that transmits the rotational force from the rotor 111 to the swash plate 112 and determines the trajectory of the tilt of the swash plate 112 by the rotor arm 141, the swash plate arm 142, the pin 143, and the projecting portion 144. Composed.
  • the hinge mechanism 140 can be constructed with a simple structure.
  • the variable displacement compressor 100 including the hinge mechanism 140 capable of transmitting a rotational force from the rotor 111 to the swash plate 112 with a simple structure and determining a tilting trajectory of the swash plate 112 is provided. Can do.
  • At least a part of 143b1 is configured to be located in a region between the two rotor arm walls 141a and 141b.
  • the pin 143 is merely loosely fitted in the holes 142a3 and 142b3, the cost can be reduced and beneficial in terms of processing costs and equipment costs.
  • a gap (clearance) is provided between the left outer wall surface 142a1 and the left inner wall surface 141a1 or between the right outer wall surface 142b1 and the right inner wall surface 141b1. Therefore, during the operation of the compressor, the swash plate arm 142 may rattle due to this gap, which may cause noise.
  • the rattling can be suppressed by increasing the machining accuracy of the inner wall surfaces 141a1, 141b1 and the wall surfaces 142a1, 142b1, and reducing the gap.
  • the cost will increase.
  • a compression reaction force from the piston 126 that is, a force in a direction away from the piston 126) acts on a region on the preceding side of R (a region on the right side of the virtual plane P in the drawing).
  • a force in the direction of pulling toward the piston 126 acts on a region on the subsequent side of the rotation direction R of the swash plate 112 (a region on the left side of the virtual plane P in the drawing). This is because the piston 126 during the compression process that moves from the bottom dead center to the top dead center via a pair of shoes 127 and 127 is connected to the outer edge of the region on the leading side in the rotational direction R of the swash plate 112. The piston 126 during the suction process that moves from the top dead center toward the bottom dead center via a pair of shoes 127 and 127 is provided at the outer edge of the rear side region of the rotation direction R of the swash plate 112. This is because they are connected.
  • the swash plate 112 is divided by the virtual plane P into an action area F1 where a compression reaction force from the piston 126 acts and a non-action area F2.
  • the swash plate 112 generally has a straight line X1 connecting the portion P1 closest to the cylinder bore 101a and the portion P2 farthest from the cylinder bore 101a in the extending direction of the axis X0 at the outer edge of the inclined swash plate 112.
  • the force which rotates the swash plate 112 acts centering on (refer FIG. 3). That is, a bias load due to the compression reaction force of the piston 126 acts on the swash plate 112.
  • the offset load due to the compression reaction force is used, and the swash plate 112 is intentionally (positively) tilted as much as the gap allows during the operation of the compressor.
  • the pin 143 assembled to the swash plate arm 142 protruding from the swash plate 112 is in contact with the inclined surface 144a of the protruding portion 144 protruding from the rotor 111, and the protruding portion 144 is A load in the extending direction of the axis X0 is received with respect to the eccentric load due to the compression reaction force acting on the swash plate 112 via the inclined surface 144a.
  • the swash plate 112 when an unbalanced load due to the compression reaction force acts on the swash plate 112, a moment is generated that rotates the swash plate 112 with a contact portion between the pin 143 and the inclined surface 144a as a fulcrum.
  • the swash plate 112 is slightly tilted about the fulcrum and is in contact with the rotor arm 141 as much as the clearance allows, and is coupled with the drive shaft 110 and the rotor 111. Rotates stably. Specifically, the swash plate 112 is slightly tilted about the fulcrum in the direction indicated by the arrow B in FIG.
  • a gap is formed between the base end portion of the left outer wall surface 142a1 and the distal end portion of the left inner wall surface 141a1.
  • the swash plate 112 is stably supported by the rotor 111 at two points of the C1 portion and the C2 portion, and rattling of the swash plate 112 is suppressed or prevented. . Therefore, it is possible to suppress or prevent the generation of noise due to the gap without increasing the processing accuracy of the inner wall surfaces 141a1 and 141b1 and the wall surfaces 142a1 and 142b1.
  • FIGS. 7 and 8 are side views of the assembly viewed from the same direction as FIG. 5 (specifically, the direction A shown in FIG. 4).
  • the projecting portion 144 has an inclined surface 144a.
  • the center position in the width direction is eccentric with respect to the virtual plane P toward the non-action region F2 side.
  • the protruding portion 144 shown in FIG. 5 is arranged so that the center position in the width direction of the inclined surface 144a is located on the virtual plane P.
  • the projecting portion 144 has a groove 144b at the center in the width direction of the inclined surface 144a.
  • a gap may be set at least in a region on the action region F1 side between the predetermined portion of the pin 143 and the inclined surface 144a of the protruding portion 144.
  • the height of the portion on the active region F1 side of the inclined surface 144a divided into two by the groove 144b from the end surface of the rotor is the rotor of the portion on the non-active region F2 side of the divided inclined surface 144a.
  • the left inner wall surface 141a1 on the non-operating region F2 side of the two swash plate arm wall portions 142a and 142b is in surface contact with the opposing left outer wall surface 142a1, as shown in FIG.
  • a tapered gap may be set between the projecting portion 144 and the pin 143 shown in FIG. 8 so as to increase from the region on the non-operation region F2 side toward the region on the operation region F1 side.
  • the inclined surface 144a may be inclined in the width direction
  • the pin 143 may be formed in a taper pin shape, or a combination thereof.
  • the pin 143 is supported by inserting the end portions 143a and 143b in the extending direction into the hole portions 142a3 and 142b3, respectively, and the hole portions 142a3 and 142b3 are respectively inclined.
  • the plate arm wall portions 142a and 142b are through holes penetrating in the wall thickness direction, the present invention is not limited to this.
  • the hole 142a3 corresponding to the swash plate arm wall 142a on the non-acting region F2 side of the two swash plate arm walls 142a and 142b may be a blind hole that stops before the left outer wall surface 142a1. Good.
  • the drive shaft 110 rotates clockwise about the axis line X0 as viewed from the end of the drive shaft 110 on the power transmission device side (external power input side, lower side in the figure). Although it rotates in the direction R, it is not limited to this and may rotate counterclockwise.
  • the working region F1 and the non-working region F2 are reversed from those in FIG. 5, and the swash plate 112 is minutely moved in the direction opposite to the arrow B in FIG. Lean on. More specifically, a gap is generated between the proximal end portion of the right outer wall surface 142b1 of the swash plate arm 142 and the distal end portion of the right inner wall surface 141b1 of the rotor arm 141 in this slightly inclined state (C1 shown in FIG. 5).
  • the distal end portion of the right outer wall surface 142b1 and the proximal end portion of the right inner wall surface 141b1 are in contact with each other, and a gap is generated between the distal end portion of the left outer wall surface 142a1 and the proximal end portion of the left inner wall surface 141a1 (FIG. 5).
  • the swash plate 112 is stably supported by the rotor 111 at two points, and rattling of the swash plate 112 is suppressed or prevented.
  • the position of the gap due to the step and the inclination direction of the tapered gap are the positions and directions described above. And reverse.
  • the present invention can be applied to a compressor equipped with an electromagnetic clutch, a clutchless compressor, and a compressor driven by an electric motor.
  • this invention is not restrict
  • Variable displacement compressor 101 Cylinder block (housing) 101a ... Cylinder bore 102 ... Front housing (housing) 104 ... Cylinder head (housing) DESCRIPTION OF SYMBOLS 110 ... Drive shaft 111 ... Rotor 112 ... Swash plate 126 ... Piston 141 ... Rotor arm 141a, 141b ... Two rotor arm wall part 141a1, 141b1 ... Inner wall surface (left inner wall surface, right inner wall surface) mutually opposed 142 ... Swash plate arms 142a, 142b ... Two swash plate arm walls 142a1 ... Wall surface (outer left wall surface) 142a2 ... tip part 142b1 ...
  • wall surface (right outer wall surface) 142b2 ... tip part 143 ... pin 143a1 ... end face 143b1 ... end face 144 ... projecting part 144a ... inclined surface X0 ... axis F1 ... action area F2 ... non-action area P ... virtual plane

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

L'invention concerne une structure d'un mécanisme d'articulation d'un compresseur à débit variable qui est simplifiée. Ce compresseur à débit variable est pourvu d'un mécanisme d'articulation (140) comprenant un bras de rotor (141), un bras de plateau oscillant (142), une broche (143) et une partie saillante (144). Le bras de rotor (141) comprend deux parties de paroi de bras de rotor (141a, 141b) qui se font face. Le bras de plateau oscillant (142) est inséré entre des surfaces de paroi interne (141a1, 141b1) du bras de rotor (141), et comprend deux parties de paroi de bras de plateau oscillant (142a, 142b) qui se font face. La broche (143) est reliée entre les deux parties d'extrémité distale (142a2, 142b2) des deux parties de paroi de bras de plateau oscillant (142a, 142b). La partie saillante (144) est disposée de manière à faire saillie dans une zone prescrite d'un rotor (111) entre les deux parties de paroi de bras de rotor (141a, 141b), et comporte une surface inclinée (144a) inclinée de telle sorte que la distance à partir d'une surface d'extrémité du rotor (111) augmente à mesure que la distance à partir du centre du rotor (111) diminue. La broche (143) vient buter contre la surface inclinée (144a).
PCT/JP2019/002606 2018-02-28 2019-01-21 Compresseur à débit variable WO2019167504A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201980012657.0A CN111699317B (zh) 2018-02-28 2019-01-21 可变容量压缩机

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-035707 2018-02-28
JP2018035707A JP7028402B2 (ja) 2018-02-28 2018-02-28 可変容量圧縮機

Publications (1)

Publication Number Publication Date
WO2019167504A1 true WO2019167504A1 (fr) 2019-09-06

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CN (1) CN111699317B (fr)
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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004108245A (ja) * 2002-09-18 2004-04-08 Toyota Industries Corp 容量可変型圧縮機
KR20060009067A (ko) * 2004-07-20 2006-01-27 주식회사 두원전자 용량 가변형 사판식 압축기

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1136389C (zh) * 1996-09-13 2004-01-28 株式会社丰田自动织机制作所 可变容量压缩机
JP4007637B2 (ja) * 1997-03-31 2007-11-14 サンデン株式会社 可変容量圧縮機
JP2008064057A (ja) * 2006-09-08 2008-03-21 Calsonic Kansei Corp 可変容量圧縮機
KR101193399B1 (ko) * 2012-06-22 2012-10-26 주식회사 두원전자 용량가변형 사판식 압축기

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2004108245A (ja) * 2002-09-18 2004-04-08 Toyota Industries Corp 容量可変型圧縮機
KR20060009067A (ko) * 2004-07-20 2006-01-27 주식회사 두원전자 용량 가변형 사판식 압축기

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CN111699317A (zh) 2020-09-22
CN111699317B (zh) 2022-05-17
JP7028402B2 (ja) 2022-03-02
JP2019152104A (ja) 2019-09-12

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