JP6271660B2 - Control valve for variable displacement compressor - Google Patents

Description

  The present invention relates to a control valve for a variable displacement compressor used in a car air conditioner or the like.

  An example of this type of control valve for a variable displacement compressor is described in Patent Document 1 (FIG. 1) below. This control valve basically includes a valve chamber 21 in which a valve port 22 is provided in a valve body 20 and a compressor, as shown in a simplified illustration of a main portion (valve body portion) in FIG. Ps inlet / outlet 27 (in this case, a vertical hole penetrating the valve body 20 up and down as shown by a broken line) is provided, and is compressed upstream (downward here) from the valve port 22. A Pd introduction port 25 communicating with the discharge chamber of the machine is provided, and a Pc inlet / outlet port 26 communicating with the crank chamber of the compressor is provided downstream of the valve port 22 (upper side in this case). In addition, a valve body (valve rod) 15 for opening and closing the valve port 22, an electromagnetic actuator having a plunger for moving the valve body 15 in the valve port opening / closing direction, and the suction pressure Ps from the compressor through the Ps inlet / outlet And a pressure-sensitive response member that urges the valve body 15 in the valve opening / closing direction in accordance with the pressure in the pressure-sensitive chamber.

  The valve body 15 includes, in order from the top, an upper insertion portion 15e, an intermediate small diameter portion 15d, and a valve port 22 that are slidably inserted into an upper guide hole 19A provided in the upper portion of the valve body 20. The lower body insertion part slidably inserted into the valve body part 15a disposed in the valve chamber 21 to be opened and closed, the lower small diameter part 15c, and the lower guide hole 19B provided in the lower part of the valve body 20. The suction pressure Ps is applied to the lower end surface of the lower fitting portion 15b.

  Here, when the outer diameter of the upper insertion portion 15e is φa, the diameter of the valve port 22 is φb, the outer diameter of the valve body portion 15a is φc, and the outer diameter of the lower insertion portion 15b is φd, φc> φb> These dimensions are set so as to satisfy the relationship of φa≈φd.

  Further, in Patent Document 2 (third embodiment thereof), a valve release passage for releasing the pressure Pc of the crank chamber to the suction chamber of the compressor through the Ps inlet / outlet is provided in the main valve body. A sub-valve element for opening and closing the relief passage in the valve, and the main valve element is slidably inserted into an upper guide hole provided in the upper part of the valve body in order from above, A small-diameter portion and a valve opening are opened and closed from the lower side, and are slidably inserted into a main valve body portion, a lower small-diameter portion and a lower guide hole provided in the lower portion of the valve body. The suction pressure Ps (or the crank chamber pressure Pc) acts on the lower end surface of the lower insertion portion, the outer diameter of the upper insertion portion is φa, and the diameter of the valve port is Assuming that φb, the outer diameter of the main valve body portion is φc, and the outer diameter of the lower fitting insertion portion is φd, the conventional example shown in FIG. Similarly, φc> φb> φa ≒ control valve for variable capacity compressors which their dimensions so as to satisfy the relation of φd is set is disclosed.

  In the conventional control valve as described above (shown in FIG. 3B), the suction pressure Ps acts downward and the crank chamber pressure Pc acts upward on the upper insertion portion 15e. , Ps≈Pc, so that they cancel out. Further, the crank chamber pressure Pc acts downward and the discharge pressure Pd acts upward on the valve body portion 15a, but Pd> Pc, so that the main valve body portion 15a faces upward (valve closing direction). The differential pressure (Pd-Pc) component acts on the. Further, the discharge pressure Pd acts downward and the suction pressure Ps acts upward on the lower insertion portion 15b. However, since Pd> Ps, the lower insertion portion 15 faces downward (valve opening direction). The differential pressure (Pd-Ps) component acts on.

  Here, Ps≈Pc, [outer diameter φc of the valve body portion]> [outer diameter φd of the lower insertion portion], so that the valve body is upward (valve closing direction), (Pd−Ps) × ( A force (valve closing force) corresponding to the pressure receiving area of the valve body portion minus the pressure receiving area of the lower insertion portion is applied.

JP 2010-185285 A Japanese Patent Application No. 2011-161121

  In the control valve for a variable displacement compressor as described above, it is desired that the crank chamber pressure Pc is controlled so as not to be affected by the discharge pressure Pd from the viewpoint of control accuracy and the like. However, when the valve is closed, it is hardly affected by the discharge pressure Pd. However, when the valve is opened, as described above, [the outer diameter φc of the valve body portion]> [the outer diameter φd of the lower insertion portion] Therefore, a force (valve closing force) corresponding to (Pd−Pc) × (pressure receiving area of the valve body portion−pressure receiving area of the lower fitting insertion portion) acts upward (valve closing direction) on the valve body. This adversely affects control. Further, if the sub-valve is not opened at the time of starting the compressor, the crank chamber pressure Pc does not drop quickly, and it becomes impossible to achieve a reduction in the time required until the discharge capacity increases.

  In the control valve, the upper insertion portion 15e and the lower insertion portion 15b of the valve body 15 are respectively inserted into the guide holes 19A and 19B provided in the upper and lower portions of the valve body so as to slide. However, since [the outer diameter φc of the valve body portion 15a]> [the outer diameter φd of the lower fitting insertion portion 15b], the valve body is inserted into the valve body from below and assembled. In the main body, a through hole 18 having a diameter larger than the outer diameter φc of the valve body portion 15a for allowing the valve body portion 15a to pass in advance is formed, and the lower fitting insertion portion 15b slides in the through hole 18. A cylindrical guide body 52 having a guide hole 19B that can be freely inserted is attached and fixed by press fitting or the like.

  As described above, the upper guide hole 19A is directly formed in the valve body without any other member, but the lower guide hole 19B is formed in the other member (tubular guide body 52) fixedly attached to the valve body. Since it is provided, the two guide holes 19A and 19B are likely to be misaligned with each other, and the slidability of the valve body (the upper fitting insertion portion 15e and the lower fitting insertion portion 15b) is lowered due to the deviation of the shaft center. However, it may cause malfunction. In order to make it difficult for malfunction to occur, the sliding surface clearance (clearance) formed between the inner peripheral surface of the guide hole and the outer peripheral surface of the insertion portion may be increased. The amount of internal leakage increases and efficiency decreases. In addition, when the clearance between the sliding surfaces is increased, large foreign matters are easily caught, and foreign matters are clogged with the clearance between the sliding surfaces, resulting in malfunctions such as the valve body not moving (locking, leaving the valve body). Furthermore, since it is necessary to retrofit another member (cylindrical guide body 52), there are also problems such as high component costs, high processing and assembly costs, and poor component assembly.

  Further, in the control valve described in Patent Document 2, if an attempt is made to set a large diameter of the relief passage in the main valve body so that the crank chamber pressure Pc can be lowered more quickly, the main valve body inevitably becomes larger. It is necessary to set the outer diameter φc of the part large. When the outer diameter of the main valve body is set to be large in this way, the pressure receiving area of the main valve body is increased, and thus the upward force (valve closing force) acting on the main valve body is further increased, making it difficult to open the valve. Thus, a large force is required to open the valve, and a problem arises in that a large-sized electromagnetic actuator must be used.

  The present invention has been made in view of the above circumstances, and an object of the present invention is for a variable displacement compressor capable of controlling the crank chamber pressure Pc with high accuracy while being hardly affected by the discharge pressure Pd. It is to provide a control valve.

  Another object of the present invention is to provide a control valve for a variable displacement compressor that can reduce the amount of leakage inside the valve, can be less prone to malfunction, and can keep parts costs and processing and assembly costs low. It is in. In addition, the sub-valve can be reliably opened when the compressor is started, and the time required for the discharge capacity to be increased when the compressor is started can be shortened without reducing the operating efficiency of the compressor. Another object of the present invention is to provide a control valve for a variable displacement compressor that can be made difficult to cause malfunction such as valve lock.

In order to achieve the above object, a control valve for a variable displacement compressor according to the present invention basically has a valve chamber provided with a valve port and a Ps inlet / outlet communicating with a suction chamber of the compressor. the with Pd introduction port communicating with the discharge chamber of the compressor on the upstream side of the valve port is provided, the valve body Pc inlet and outlet is provided which communicates with the crank chamber of the compressor from the valve port to the downstream A main valve body for opening and closing the valve port, an electromagnetic actuator having a plunger for moving the main valve body in the valve port opening and closing direction, and a suction pressure Ps from the compressor through the Ps inlet / outlet And a pressure sensitive response member that urges the main valve body in the valve opening / closing direction according to the pressure in the pressure sensitive chamber, and the pressure Pc in the crank chamber is set to Ps. In-valve escape passage for escaping to the suction chamber of the compressor via the inlet / outlet When provided in the main valve body and a sub-valve body for opening and closing the valve escape passage is provided, and when the plunger is continuously moved upward from the lowest position by the suction force of the electromagnetic actuator, wherein together with said plunger with auxiliary valve body moves upward while closing the passage relief in said valve, said main valve body is moved upward so as to follow the sub valve body, the main valve After the valve opening is closed by the body, when the plunger is further moved upward, the sub-valve element opens the escape passage in the valve and urges the main valve element in the valve closing direction. Until the amount of upward movement from the lowest position of the plunger reaches the first lift amount, the main valve body is closed so as to follow the plunger by the biasing force of the valve closing spring. valve When the upward movement amount reaches the first lift amount, the valve port is closed by the main valve body, and the upward movement amount is further increased by a predetermined amount from the first lift amount. Until the lift amount reaches two lifts, the sub-valve element is pulled up by the predetermined amount by the plunger so that the escape passage in the valve is opened, a latching portion is provided at the lower part of the plunger, and the main valve A locking portion that is hooked by the latching portion is provided at the top of the body, and the first lift amount is determined by the main valve when viewed in a state where the plunger, the main valve body, and the sub-valve body are in the lowest lowered position. The vertical distance between the main valve body part of the body and the valve port, the predetermined amount is the vertical distance between the latching part of the plunger and the locking part of the main valve body, The second lift amount is obtained by adding the predetermined amount to the first lift amount. It is characterized in that it is set for each lift amount .

  In the control valve for a variable displacement compressor according to the present invention, when the plunger continuously moves upward from the lowest position by the suction force of the electromagnetic actuator, the sub-valve element closes the in-valve relief passage together with the plunger. After the valve is closed by the main valve body and the plunger further moves upward, the sub-valve opens the valve escape passage, so that the crank chamber pressure Pc Since it is escaped to the suction chamber through the two passages of the in-valve escape passage, the time required until the discharge capacity becomes large at the time of starting the compressor can be greatly shortened.

  In addition, [the outer diameter φc of the valve body portion] ≈ [the outer diameter φd of the lower insertion portion]> [the diameter φb of the valve opening]> [the outer diameter φa of the upper insertion portion]. Therefore, the upward force (valve closing force) acting on the valve body part and the downward force (valve opening force) acting on the lower insertion part are offset, so that when the main valve is opened, As a result, the control accuracy and the like of the crank chamber pressure Pc can be improved.

  In the control valve for the variable displacement compressor described above, during normal operation (Pd → Pc control), since the escape passage in the valve is closed by the sub-valve, the operating efficiency of the compressor does not decrease. . Furthermore, the valve opening operation of the sub-valve element is performed by moving the plunger upward by the suction force of the solenoid part without relying on the expansion / contraction force of the bellows device. The reliability can be improved.

  Further, a minute foreign matter is clogged in a sliding surface gap formed between the main valve body and its guide hole (inner wall surface), and the main valve body cannot be moved upward only by the urging force of the valve closing spring. In this embodiment, the plunger is pulled up by the suction force of the solenoid part, and the main valve is pulled up by the inner hook-shaped hooking part of the plunger, even if the situation (operation failure such as valve lock, main valve body leaving, etc.) is likely to occur. Since the main valve body can be pulled up by hooking the hook-shaped locking part of the body, it is difficult to cause malfunctions such as valve locking and leaving the main valve body.

  In addition, since the upper guide hole and the lower guide hole are both formed directly in the single valve body without any other member, the lower guide hole is separately attached to the valve body as in the conventional example. Compared with the case where it is formed in the member, the two guide holes are less likely to be misaligned, and the slidability of the valve body (the upper insertion portion and the lower insertion portion) is improved.

  Further, since the shaft misalignment hardly occurs, the sliding surface gap (clearance) formed between the inner peripheral surface of the guide hole and the outer peripheral surface of the fitting portion can be reduced, so that the amount of leakage inside the valve In addition, it is difficult to entrap large foreign matter, and it is difficult to cause malfunctions such as the foreign matter being clogged in the gap between the sliding surfaces and the valve element not moving (locking, leaving the valve element). Furthermore, since it is not necessary to retrofit the other member (cylindrical guide body), the component cost and the processing / assembling cost can be kept low, and the component assembling property and the like are improved.

1 is a longitudinal sectional view showing a first embodiment of a control valve for a variable displacement compressor according to the present invention. The enlarged view of the valve main-body part of the control valve shown by FIG. BRIEF DESCRIPTION OF THE DRAWINGS The principal part schematic diagram used for description of the difference between this invention 1st Example (A) and a prior art example (B). The longitudinal cross-sectional view which shows the state (at the time of normal control) of the main valve of the 2nd Example of the control valve for variable displacement type compressors which concerns on this invention: Open and sub valve | bulb. The enlarged view of the valve main-body part of the control valve shown by FIG. The longitudinal cross-sectional view which shows the state (at the time of compressor starting) of the main valve of the 2nd Example of the control valve for variable displacement type compressors which concerns on this invention: Closed and a subvalve. (A) is the principal part enlarged view of FIG. 4, (B) is the principal part enlarged view of FIG. (A) is a figure which shows the refrigerant | coolant pressure distribution condition between the compressor and control valve at the time of normal control, (B) is a figure which shows the refrigerant | coolant pressure distribution condition between the compressor and control valve at the time of compressor starting . The graph which shows the relationship between the discharge pressure Pd of the control valve of this invention Example, and valve closing force Pt.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing a first embodiment of a control valve for a variable displacement compressor according to the present invention. FIG. 2 is an enlarged view of a valve main body portion of the control valve shown in FIG. ), (B) are schematic views of the main part for explaining the difference between the first embodiment of the present invention and the conventional example. In the control valve 1 of the illustrated first embodiment, portions corresponding to the respective portions of the control valve 5 of the conventional example shown in FIG.

  The illustrated control valve 1 includes a valve body 15 integrally connected to an operating rod 14, a valve body 20 having an upper guide hole 19A and a lower guide hole 19B having a central axis O as a common central axis, an electromagnetic type And an actuator 30. The valve body 20 has a valve chamber 21 in which a valve port (valve seat portion) 22 that is opened and closed by a valve body portion 15a of the valve body 15 is provided between the upper guide hole 19A and the lower guide hole 19B. A plurality of Pd inlets 25 with a filter 25A for introducing a refrigerant having a discharge pressure Pd from the compressor are provided on the outer peripheral portion (upstream side of the valve port 22) of the valve chamber 21, and the downstream side of the valve port 22 Further, a Pc inlet / outlet 26 with a filter 26A communicating with the crank chamber of the compressor is provided.

  The electromagnetic actuator 30 includes a coil 32 having a connector portion 31 for energization excitation, a cylindrical stator 33 disposed on the inner peripheral side of the coil 32, and a concave section that is press-fitted and fixed to the inner periphery of the lower end portion of the stator 33. Pipe-shaped suction element 34, pipe 35 with flange 35a whose upper end is joined to the outer periphery (step part) of the lower end of stator 33 by TIG welding, and the upper and lower sides of pipe 35 below the suction element 34 A plunger 37 slidably disposed in the direction and a cylindrical housing 60 with a bottomed hole disposed so as to cover the outer periphery of the coil 32 are provided. Here, the part which consists of the coil 32, the stator 33, the attractor 34, etc. except the plunger 37 among the electromagnetic actuators 30 is called solenoid part 30A.

  Further, an adjusting screw 65 having a hexagonal hole is screwed onto the stator 33, and a suction pressure Ps of the compressor is interposed between the adjusting screw 65 and the suction element 34 on the inner peripheral side of the stator 33. Is formed in the pressure sensing chamber 45. The pressure sensing chamber 45 includes a bellows 41, a reverse convex upper stopper 42, a reverse concave lower stopper 43, and a compression coil. A bellows body 40 comprising a spring 44 is disposed, and further, a compression coil that urges the bellows body 40 and the suction element 34 in a direction in which the bellows body 40 contracts (a direction in which the bellows body 40 is compressed toward the adjustment screw 65). The spring 46 is contracted. Also, a stepped operating rod 14 that penetrates the suction element 34 is disposed between the lower stopper 43 (reverse recess) of the bellows body 40 and the plunger 37 (recess 37b), and further, the suction element A valve-opening spring 47 comprising a compression coil spring that urges the operating rod 14 and the plunger 37 downward (in the valve-opening direction) is mounted between the upper end 34 of the large-diameter portion 14c of the operating rod 14 and the plunger. Yes.

  The valve body 15 integrally connected to the actuating rod 14 is provided on the bottom of the plunger 37 and the upper end convex portion 15i to which the lower end portion (concave hole portion) 14b of the actuating rod 14 is connected and fixed by press fitting or the like in order from the top. An annular groove portion 15j into which the engaging portion 38 is fitted, an upper insertion portion 15e slidably inserted into the upper guide hole 19A, an intermediate small diameter portion 15d having a smaller diameter than the upper insertion portion 15e, and a valve port 22 Slided to the valve body portion 15a having a larger diameter than the upper fitting insertion portion 15e, the lower diameter portion 15c having a smaller diameter than the valve body portion 15a, and the lower guide hole 19B disposed in the valve chamber 21 to be opened and closed from the lower side. A lower insertion portion 15b that can be freely inserted is provided, and suction pressure Ps acts on the lower end surface of the lower insertion portion 15b.

  A locking portion provided at the bottom of the plunger 37 in the annular groove portion (small diameter portion) 15j below the connecting and fixing portion between the upper end convex portion 15i of the valve body 15 and the lower end portion (concave hole portion) 14b of the operating rod 14. 38 is fitted, and the valve body 15 and the plunger 37 can be moved up and down integrally.

  Further, the valve body 20 is provided with a Ps inlet / outlet (passage) 27 composed of a straight upper and lower through hole in order to guide the suction pressure Ps to the pressure sensing chamber 45 (bellows body 40). More specifically, a plunger chamber 58 in which the plunger 37 is disposed is provided above the upper guide hole 19A in the valve body 20 and below the pressure sensing chamber 45, and the upper end of the Ps inlet / outlet 27 is the plunger chamber 58. The lower end of the valve body 20 is opened to the lower end surface of the valve body 20 (Ps introduction chamber 88 described later).

  Further, a lower end flange 35a of the pipe 35 is placed on the upper end portion of the valve body 20 via an O-ring 57, and a short portion with a flange 56a is provided between the flange 35a and the coil 32. A cylindrical pipe holder 56 is interposed, and the flange portions 35 a and 56 a are fastened and fixed together by an upper end outer periphery caulking portion 29 of the valve body 20. Further, the bottom portion 61 with a hole of the housing 60 is press-fitted and fixed to the upper end portion of the pipe holder 56, and the upper end portion 62 of the housing 60 is caulked and fixed on the flange-shaped portion 31 c of the connector portion 31. An O-ring 66 is interposed between the connector part 31 and the coil 32. A concave portion 31a is formed at the lower center of the connector portion 31. The concave portion 31a is formed with a convex portion 31b fitted into the hexagonal hole of the adjusting screw 65. The stator 33 and the adjusting screw are formed in the concave portion 31a. The upper part of 65 is inserted.

  In addition to the above configuration, in the control valve 1 of the first embodiment, as shown in FIGS. 2 and 3A, the outer diameter of the upper fitting portion 15e of the main valve body 15 is φa, the valve opening 22 is φb, the outer diameter of the main valve body portion 15a is φc, and the outer diameter of the lower insertion portion 15b is φd, [the outer diameter φc of the main valve body portion 15a] ≈ [of the lower insertion portion 15b] These dimensions are set so as to satisfy the relationship of [Outer Diameter φd]> [Diameter φb of Valve Port 22]> [Outer Diameter φa of Upper Insertion Part 15e].

  The control valve 1 having such a configuration is assembled in a valve mounting hole (stepped hole) 80 formed in the vicinity of the swash plate chamber in the body housing 100 of the variable capacity compressor. A snap ring (C-shaped ring) 81 for preventing removal is attached to the upper part of the valve mounting hole 80, and this snap ring 81 is brought into contact with the upper end portion (caulking portion) 62 of the housing 60. Further, the body housing 100 is provided with a Pd introduction port 25, a Pc inlet / outlet 26, and a Pd passage 92, a Pc passage 93, and a Ps passage 91 communicating with the Ps inlet / outlet 27 (Ps introduction chamber 88). . In addition, O-rings 82, 83, and 84 are disposed at important points between the outer peripheral surface of the control valve 1 and the inner peripheral surface of the valve mounting hole 80 so that Pd, Pc, and Ps do not leak. .

  A Ps introduction chamber 88 is provided between the bottom (lower part) of the valve mounting hole 80 and the lower end of the valve body 20, and the suction pressure Ps introduced into the Ps introduction chamber 88 via the Ps passage 91 is It acts on the lower end surface of the body 15 (the lower insertion portion 15b), is led to the plunger chamber 58 and the pressure sensing chamber 45 via the Ps inlet / outlet 27, and is connected to the main valve body 15 (the upper insertion portion 15e). ) Acts on the upper end surface.

  Under such a configuration, the valve opening is similar to that of the conventional example in that the plunger 37 is attracted by the solenoid portion 30A including the coil 32, the stator 33, the attractor 34, and the like, and the biasing force ( (Extension force, contraction force), biasing force by the valve opening spring 47 and the coil spring 46, force in the valve opening direction acting on the main valve body 15 and force in the valve closing direction, and depending on the valve opening degree Thus, the crank chamber pressure Pc of the compressor is adjusted, and accordingly, the inclination angle of the swash plate of the compressor and the stroke of the piston are adjusted to increase or decrease the discharge capacity. Under such a configuration, the valve opening is similar to that of the conventional example in that the plunger 37 is attracted by the solenoid portion 30A including the coil 32, the stator 33, the attractor 34, and the like, and the biasing force ( (Extension force, contraction force), biasing force by the valve opening spring 47 and the coil spring 46, force in the valve opening direction acting on the main valve body 15 and force in the valve closing direction, and depending on the valve opening degree Thus, the crank chamber pressure Pc of the compressor is adjusted, and accordingly, the inclination angle of the swash plate of the compressor and the stroke of the piston are adjusted to increase or decrease the discharge capacity.

  In the control valve 1 for the variable displacement compressor of the first embodiment having such a configuration, [the outer diameter φc of the valve body portion 15a] ≈ [the outer diameter φd of the lower fitting insertion portion 15b]> [valve port] 22] [diameter φb]> [outer diameter φa of the upper insertion portion 15e], the dimensions are set so that the upper insertion portion 15e of the valve body 15 has a suction pressure Ps downward. And the crank chamber pressure Pc acts upward, but since Ps≈Pc, they are canceled out. Further, the crank chamber pressure Pc acts downward and the discharge pressure Pd acts upward on the valve body portion 15a, but Pd> Pc, so that the main valve body portion 15a faces upward (valve closing direction). The differential pressure (Pd-Pc) component acts on the. In addition, the discharge pressure Pd acts downward and the suction pressure Ps acts upward on the lower insertion portion 15b, but since Pd> Ps, the lower insertion portion 15b faces downward (valve opening direction). The differential pressure (Pd-Ps) component acts on.

  Here, since Ps≈Pc and [outer diameter φc of the main valve body portion] ≈ [outer diameter φd of the lower insertion portion], an upward force (valve closing force) acting on the main valve body portion 15a. And the downward force (valve opening force) acting on the lower insertion portion 15b is offset. For this reason, even when the main valve 11 is opened, it is less affected by the discharge pressure Pd. As a result, the control accuracy of the crank chamber pressure Pc can be improved.

  Further, since both the upper guide hole 19A and the lower guide hole 19B are directly formed in the single valve body 20 without any other member, the lower guide hole 19A and the lower guide hole 19B are lower as in the conventional example shown in FIG. Compared to the case where the side guide hole 19B is formed in another member (cylindrical guide body 52) retrofitted to the valve body 20, the two guide holes 19A and 19B are less likely to be misaligned, and the valve body 15 The slidability of (the upper insertion part 15e and the lower insertion part 15b) becomes favorable.

  Further, since the shaft misalignment hardly occurs, the sliding surface gap (clearance) formed between the inner peripheral surface of the guide hole and the outer peripheral surface of the fitting portion can be reduced, so that the amount of leakage inside the valve In addition, it is difficult to entrap large foreign matter, and it is difficult to cause malfunctions such as the foreign matter being clogged in the gap between the sliding surfaces and the valve element not moving (locking, leaving the valve element). Furthermore, since it is not necessary to retrofit the other member (cylindrical guide body 52), the component cost and the processing / assembling cost can be kept low, and the component assembling property and the like are also improved.

  4 and 6 are longitudinal sectional views showing a second embodiment of the control valve for a variable displacement compressor according to the present invention, respectively. FIG. 4 shows a state in which the main valve is open and the subvalve is closed (normal control). FIG. 6 shows the main valve: closed and the subvalve: open (when the compressor is started). 5 is an enlarged view of the valve body portion of FIG. 4, FIGS. 7 (A) and 7 (B) are enlarged views of main portions of FIGS. 4 and 6, respectively, and FIG. 8 (A) is a compressor during normal control. FIG. 8B is a diagram showing a refrigerant pressure distribution state between the compressor and the control valve at the time of starting the compressor. In the control valve 2 of the second embodiment, portions corresponding to the respective portions of the control valve 1 of the first embodiment described above are denoted by common reference numerals.

  The control valve 2 in the illustrated second embodiment includes a valve body 20 provided with a valve port 22, a main valve body 15 for opening and closing the valve port 22, and moving the main valve body 15 in the valve port opening / closing direction. And an bellows device 40 as a pressure-sensitive response member.

  The electromagnetic actuator 30 includes a coil 32 for energizing excitation, a connector head 31 attached to the upper side of the coil 32, a stator 33 and an attractor 34 disposed on the inner peripheral side of the coil 32, and a stator 33 and an attractor 34. Guide pipe 35 whose upper end is joined by TIG welding to the outer periphery (step part) of the lower end of the bottom of the guide pipe 35, and is bottomed and slidably disposed on the inner peripheral side of the guide pipe 35 in the vertical direction. A cylindrical plunger 37, a stepped cylindrical housing 60 that is externally inserted into the coil 32 and the connector head 31, and a lower end portion of the housing 60 and the guide pipe 35. The holder 29 for fixing to the upper part of the is provided. Here, the part which consists of the coil 32, the stator 33, the attractor 34, etc. except the plunger 37 among the electromagnetic actuators 30 is called solenoid part 30A.

  An adjustment screw 65 with a hexagonal hole is screwed onto the top of the stator 33, and the suction pressure of the compressor 100 is between the adjustment screw 65 and the suction element 34 on the inner peripheral side of the stator 33. A pressure-sensitive chamber 45 into which Ps is introduced is formed. In the pressure-sensitive chamber 45, a bellows 41, a reverse convex upper stopper 42, a reverse concave lower stopper 43, and a compression member as pressure sensitive response members are formed. A bellows device 40 including a coil spring 44 is disposed. Further, an intermediate small diameter portion 17d of the sub-valve element 17 described later is fitted into the recess of the lower stopper 43, and between the lower stopper 43 and the suction element 34. A compression coil spring 46 that biases the bellows device 40 in a contracting direction is mounted.

  A latching member having an insertion hole 36b for inserting a lower small diameter portion 17b of the sub-valve element 17 to be described later and a latching portion 36a for latching the intermediate large diameter latching portion 17c at the center of the inner periphery of the plunger 37. 36 is fixed by press fitting or the like.

  Further, a reverse cone that biases the sub-valve body 17 and the plunger 37 downward (in the valve opening direction) between the suction element 34 and an intermediate large-diameter locking portion 17c (plunger 37) of the sub-valve body 17 described later. A cylindrical compression coil spring (valve opening spring) 47 is mounted.

  The main valve body 15 includes a lower end small diameter portion 15s, a lower fitting insertion portion 15b, a lower small diameter portion 15c, a main valve body portion 15a, an intermediate small diameter portion 15d, an upper fitting insertion portion 15e, an upper small diameter portion 15f in order from the bottom. And a hook-like locking portion 15k, and a through-hole 16A constituting a part of the valve escape passage 16 is provided in the interior thereof so as to penetrate in the vertical direction. The upper end portion is a sub-valve seat portion 23 with which the sub-valve portion 17a of the sub-valve body 17 is separated from and contacting. The intermediate small diameter portion 15d of the main valve body 15 is provided with a plurality of lateral holes 16s.

  An inner hook-shaped hooking portion 37k provided on the bottom of the plunger 37 is loosely fitted to the upper small diameter portion 15f of the main valve body 15, and the inner hook-shaped hooking portion 37k is hooked to the hook-shaped engagement of the main valve body 15. When the plunger 37 has a smaller diameter than the stopper 15k and is moved upward with respect to the main valve body 15, the hook-like locking part 15k is hooked by the inner hook-like hook 37k and the main valve 15 is lifted. It is supposed to be.

  On the other hand, a convex stopper portion 24 for restricting the lowest position of the plunger 37 is provided in the upper half of the valve body 20, and the suction of the compressor 100 is provided on the outer periphery of the convex portion of the stopper portion 24. A pressure Ps inlet / outlet chamber 28 is formed, and a plurality of Ps inlets / outlets 27 are formed on the outer periphery thereof. The suction pressure Ps introduced into the inlet / outlet chamber 28 from the Ps inlet / outlet 27 is a peripheral wall portion of the plunger 37. A plurality of lateral holes 37 s formed in the gap, a gap formed between the lower small diameter portion 17 b of the auxiliary valve body 17 and the insertion hole 36 b, a gap formed between the outer periphery of the plunger 37 and the guide pipe 35, etc. Is introduced into the pressure-sensitive chamber 45.

  An upper guide hole 19A into which the upper portion of the main valve body 15 is slidably fitted is formed at the center of the stopper portion 24, and the lower end portion of the upper guide hole 19A is a main valve of the main valve body 15 described later. It is a valve port 22 (valve seat portion) that is opened and closed by the body portion 15a. Here, the main valve part 11 is comprised by the main valve body part 15a and the valve port 22. FIG.

  The sub-valve body 17 includes, in order from the bottom, a flat sub-valve body portion 17a that is separated from and in contact with the sub-valve seat portion 23 to open and close the valve escape passage 16, a lower small-diameter portion 17b, an intermediate large-diameter locking portion 17c, The auxiliary valve portion 12 is composed of the auxiliary valve seat portion 23 and the auxiliary valve body portion 17a.

  Further, an insertion hole 18 having a diameter larger than that of the upper guide hole 19 </ b> A for allowing the main valve body 15 to be inserted at the time of assembly is provided in the central portion of the lower half of the valve body 20. A stepped cylindrical guide tube member 13 is inserted into and fixed to the lower portion of the insertion hole 18 by press fitting or the like. The guide cylinder member 13 includes, in order from the top, a thin small diameter portion 13a, a thick large diameter portion 13b, and an inner flange-shaped spring receiving portion 13c, and the inner periphery thereof is a lower insertion portion 15b of the main valve body 15. The lower guide hole 19B is slidably inserted. A valve closing spring 50 formed of a compression coil spring is compressed between the inner flange-shaped spring receiving portion 13c and a step portion (step portion) 15g between the lower end small diameter portion 15s of the main valve body 15 and the lower fitting insertion portion 15b. It is disguised.

  A portion of the insertion hole 18 above the guide tube member 13 and below the valve port 22 is a valve chamber 21. The valve chamber 21 has a Pd introduction port 25 communicating with the discharge chamber 106 of the compressor 100. Are opened.

  Further, a lid-like member 48 that functions as a filter is fixed to the lower end portion of the valve body 20 by screwing or the like, and the crank-side of the compressor 100 is located above the lid-like member 48 and below the main valve body 15. It is a Pc entrance / exit chamber (entrance / exit) 26 communicating with the chamber 104.

  In the present embodiment, the pressure Pc of the crank chamber 104 is supplied to the compressor 100 via the Ps inlet / outlet 27 in the through relief hole 16A formed in the main valve body 15, the plunger 37, the lateral hole 37s, the inlet / outlet chamber 28, and the like. An in-valve escape passage 16 is formed to escape to the suction chamber 107.

  Further, when the sub-valve body portion 17a of the sub-valve body 17 comes into contact with and separates from the sub-valve seat portion 23 that is the upper edge of the through-hole 16A of the main valve body 15, the in-valve relief passage 16 is opened and closed. It is like that.

  Here, in the control valve 2 of the present embodiment, as shown in FIGS. 4 and 7A, the plunger 37, the main valve body 15, and the sub-valve body 17 are in the lowest lowered position (the plunger 37 of the plunger 37). The lowermost end surface is in contact with the stopper portion 24, the main valve portion 11 is fully open, and the sub-valve portion 12 is fully closed) between the main valve body portion 15a of the main valve body 15 and the valve port 22 (valve seat portion). Is the first lift amount Lv, and the separation distance between the inner hook-shaped hooking portion 37k of the plunger 37 and the hook-shaped locking portion 15k of the main valve body 15 is a predetermined amount La, and the maximum distance of the plunger 37 is The lift amount Lp (the lift amount from the lowest position of the plunger 37 to the highest position) is the first lift amount Lv + the predetermined amount La = the second lift amount.

  In addition to the above configuration, in the control valve of the present embodiment, as shown in FIG. 5, the outer diameter of the upper fitting portion 15e of the main valve body 15 is φa, the diameter of the valve port 22 is φb, and the main valve body When the outer diameter of the portion 15a is φc and the outer diameter of the lower fitting portion 15b is φd, [the outer diameter φc of the main valve body portion 15a] ≈ [outer diameter φd of the lower fitting portion 15b]> [valve port 22 The diameters are set so as to satisfy the relationship of [the diameter φb]> [the outer diameter φa of the upper fitting portion 15e].

Next, the operation of the control valve 2 will be described.
During normal control (Pd → Pc control), the lift amount of the plunger 37 is set to be a little greater than the first lift amount Lv, and when the compressor is started, the lift amount of the plunger 37 is equal to the second lift amount Lp. It is said.

  Specifically, during normal control (Pd → Pc control), when the solenoid portion 30A including the coil 32, the stator 33, the attractor 34, and the like is energized, the plunger 37 is attracted to the attractor 34. Accordingly, the intermediate large-diameter locking portion 17c of the sub-valve body 17 is locked to the latching portion 36a of the latching member 36 fixed to the plunger 37, so that the sub-valve body 17 is integrated with the plunger 37 in the upward direction. While moving, following this movement, the main valve body 15 is moved upward (in the valve closing direction) by the urging force of the valve closing spring 50. On the other hand, the suction pressure Ps introduced from the compressor 100 to the Ps inlet / outlet 27 is introduced from the inlet / outlet chamber 28 into the pressure sensing chamber 45 through the lateral hole 37s of the plunger 37 and the like, and the bellows device 40 (the inside is a vacuum pressure). Expands and contracts according to the pressure in the pressure sensing chamber 45 (suction pressure Ps) (contracts when the suction pressure Ps is high and contracts when the pressure is low), and the displacement is applied to the main valve body 15 via the plunger 37 and the subvalve body 17. Accordingly, the valve opening degree (the separation distance between the valve port 22 and the main valve body 15a) is adjusted.

  That is, the valve opening degree is determined by the attraction force of the plunger 37 by the solenoid portion 30A composed of the coil 32, the stator 33, the attractor 34, etc., the urging force (extension force, contraction force) of the bellows device 40, the valve closing spring 50, The pressure Pc of the crank chamber 104 is determined by the urging force of the valve opening spring 47 and the coil spring 46, the force in the valve opening direction acting on the main valve body 15, and the force in the valve closing direction. Accordingly, the inclination angle of the swash plate 102 of the compressor 100 and the stroke of the piston 105 are adjusted, and the discharge capacity is increased or decreased.

  In this case, the main valve body 15 is always urged upward by the urging force of the valve closing spring 50, and the sub valve body 17 is always urged downward by the urging force of the valve opening spring 47. The valve body portion 17 a is pressed against the sub valve seat portion 23 (the sub valve portion 12 is closed), and the valve relief passage 16 is blocked in the main valve body 15. Therefore, the crank chamber pressure Pc is not released to the suction chamber 107 through the in-valve escape passage 16.

  On the other hand, at the time of starting the compressor, the solenoid portion 30A is energized and energized, and the plunger 37 is attracted to the attractor 34. The sub-valve body 17 moves upward together with the plunger 37 and follows this upward movement. After the main valve body 15 is moved upward and the valve port 22 is closed by the main valve body portion 15a of the main valve body 15, the plunger 37 is further moved upward, whereby the sub-valve body is moved. 17 is configured to open the valve relief passage 16.

  More specifically, until the upward movement amount of the plunger 37 reaches the first lift amount Lv, the main valve body 15 follows the upward movement of the plunger 37 and the sub-valve body 17 by the urging force of the valve closing spring 50. When the amount of upward movement reaches the first lift amount Lv, the valve port 20 is closed by the main valve body 15a of the main valve body 15, and the main valve 11 is closed. The plunger 37 is further moved upward by the predetermined amount La. In other words, after the upward movement amount of the plunger 37 reaches the first lift amount Lv, the inner hook-shaped hooking portion 37k of the plunger 37 is locked to the hook-shaped locking portion 15k of the sub-valve body 17. The sub-valve body 17 is lifted by the predetermined amount La (first lift amount Lv + predetermined amount La = second lift amount). In this case, since the main valve body 15 remains stationary while being closed, the sub-valve body portion 17a of the sub-valve body 17 is lifted by a predetermined amount La from the sub-valve seat portion 23, and thereby the in-valve escape passage. 16 is opened.

  Thus, in the control valve 2 of the present embodiment, when the compressor is started, the pressure Pc in the crank chamber 104 is released to the suction chamber 107 through the two passages of the in-machine escape passage 108 and the in-valve escape passage 16. Therefore, the time required for the discharge capacity to increase at the time of starting the compressor can be significantly shortened compared to the conventional one.

  Further, during normal operation (Pd → Pc control), the in-valve escape passage 16 is closed by the sub-valve element 17, so that the operating efficiency of the compressor does not decrease.

  Further, the valve opening operation of the auxiliary valve body 17 is performed by moving the plunger 37 upward by the suction force of the solenoid part 30A without depending on the expansion / contraction force of the bellows device. The valve can be opened reliably, and the reliability is improved.

  Further, the main valve body 15 can be moved only by the urging force of the valve closing spring 50 because, for example, a minute foreign matter is clogged in the sliding surface gap formed between the main valve body 15 and the guide holes (inner wall surfaces) 19A and 19B. In the present embodiment, even when a situation in which the valve does not move upward (malfunctions such as valve lock and main valve body leaving) is likely to occur, in this embodiment, the plunger 37 is pulled up by the suction force of the solenoid portion 30A, Since the main valve body 15 can be pulled up by hooking the hook-shaped locking portion 15k of the main valve body 15 with the inner hook-shaped hooking section 37k, it is difficult to cause malfunction such as valve lock and leaving the main valve body.

  In addition to the above configuration, [the outer diameter φc of the main valve body 15a] ≈ [the outer diameter φd of the lower fitting portion 15b]> [the diameter φb of the valve port 22]> [the outer diameter φa of the upper fitting portion 15e] Since these dimensions are set so as to satisfy this relationship, the suction pressure Ps acts downward and the crank chamber pressure Pc acts upward on the upper insertion portion 15e of the main valve body 15, Since Ps≈Pc, they are canceled out. In addition, the crank chamber pressure Pc acts downward and the discharge pressure Pd acts upward on the main valve body 15a, but since Pd> Pc, the main valve body 15a faces upward (valve closing direction). ) Acts on the differential pressure (Pd-Pc). In addition, the discharge pressure Pd acts downward on the lower insertion portion 15b and the crank chamber pressure Pc acts upward, but since Pd> Pc, the lower insertion portion 15b faces downward (valve opening direction). The differential pressure (Pd-Pc) component acts on the.

  Here, since [the outer diameter φc of the main valve body portion] ≈ [the outer diameter φd of the lower fitting insertion portion], the upward force (valve closing force Pt) acting on the main valve body portion 15a and the lower fitting are set. The downward force (valve opening force) acting on the insertion portion 15b is offset. For this reason, even when the main valve 11 is opened, it is less affected by the discharge pressure Pd. As a result, the control accuracy of the crank chamber pressure Pc can be improved.

  Further, even when the diameter of the valve body escape passage 16A is set large and the outer diameter φc of the main valve body portion is also increased so that the crank chamber pressure Pc can be lowered more quickly, the valve closing force Pt is shown in FIG. As described above, even if the discharge pressure Pd increases, the discharge pressure Pd is maintained at a substantially constant value (appropriate load). Therefore, it is not difficult to open the valve, and the conventional electromagnetic actuator can be used as it is. .

  Further, since the outer diameter φc of the main valve body portion 15a and the outer diameter φd of the lower fitting insertion portion 15b are set to be substantially the same and become the maximum diameter of the main valve body 15, the main valve body is conventionally provided. Only the outer diameter φc of the portion 15a is easier to process than those having the maximum diameter, and the processing time and processing cost can be reduced.

  In the control valve 2 of the second embodiment, the lower guide hole 19B into which the lower fitting portion 15b of the main valve body 15 is slidably fitted is provided by another member (guide cylinder member) retrofitted to the valve body 20. 13), but it is not always necessary to do this, and the lower guide hole 19B can be formed as a single unit without using any other member together with the upper guide hole 19A, like the control valve 1 of the first embodiment. The valve body 20 may be formed directly, and in this way, the two guide holes 19A and 19B are less likely to be misaligned, and the valve body 15 (the upper insertion portion 15e and the lower insertion portion are inserted). The slidability of the part 15b) becomes good.

  Further, since the shaft misalignment hardly occurs, the sliding surface gap (clearance) formed between the inner peripheral surface of the guide hole and the outer peripheral surface of the fitting portion can be reduced, so that the amount of leakage inside the valve In addition, it is difficult to entrap large foreign matter, and it is difficult to cause malfunctions such as the foreign matter being clogged in the gap between the sliding surfaces and the valve element not moving (locking, leaving the valve element). Furthermore, since it is not necessary to retrofit the other member (guide cylinder member 13), the component cost and the processing / assembling cost can be kept low, and the component assembling property and the like are also improved.

1, 2 Variable displacement compressor control valve 11 Main valve part 12 Sub valve part 15 Main valve body 15a Valve body part 15b Lower insertion part 15c Lower small diameter part 15d Intermediate small diameter part 15e Upper insertion part 16 Relief passage 17 Secondary Valve body 19A Upper guide hole 19B Lower guide hole 20 Valve body 21 Valve chamber 22 Valve port 25 Pd inlet 26 Pc inlet / outlet 27 Ps inlet / outlet 30 Electromagnetic actuator 30A Solenoid part 37 Plunger 40 Bellows device (pressure sensitive member)
45 Pressure sensing chamber 58 Plunger chamber

Claims (1)

Has a Ps inlet and outlet which communicates with the suction chamber of the valve the valve port is provided chamber and the compressor, together with Pd inlet is provided which communicates with the discharge chamber of the compressor from the upstream side the valve port, the valve A valve body provided with a Pc inlet / outlet communicating with the crank chamber of the compressor downstream from the port, a main valve body for opening and closing the valve port, and moving the main valve body in the valve port opening / closing direction An electromagnetic actuator having a plunger for pressure, a pressure sensing chamber into which suction pressure Ps is introduced from the compressor through the Ps inlet / outlet, and opening and closing the main valve body according to the pressure in the pressure sensing chamber A pressure sensitive member that biases in the direction, and a valve relief passage is provided in the main valve body for allowing the pressure Pc of the crank chamber to escape to the suction chamber of the compressor via the Ps inlet / outlet. And a sub-valve element for opening and closing the relief passage in the valve. ,
When the plunger is continuously moved upward from the lowest position by the suction force of the electromagnetic actuator, the sub-valve element moves upward together with the plunger with the escape passage in the valve closed. together with the main valve body is moved upward so as to follow the sub valve body, after the valve port by the main valve body are closed, further wherein the plunger is moved upward, the The sub-valve element opens the escape passage in the valve ;
A valve-closing spring that urges the main valve body in a valve-closing direction, and the main valve body of the valve-closing spring is moved until the upward movement amount of the plunger from the lowest position reaches the first lift amount. When the urging force moves in the valve closing direction so as to follow the plunger, and when the upward movement amount reaches the first lift amount, the valve port is closed by the main valve body, and further, the upward movement amount. Until the second lift amount is larger by a predetermined amount than the first lift amount, the sub-valve body is pulled up by the predetermined amount by the plunger so that the in-valve escape passage is opened,
A latching portion is provided at a lower portion of the plunger, and a latching portion to be hooked by the latching portion is provided at an upper portion of the main valve body, so that the plunger, the main valve body, and the sub-valve body are in the lowest lowered position. In a certain state, the first lift amount is a vertical separation distance between the main valve body portion of the main valve body and the valve port, and the predetermined amount is the latching portion of the plunger and the main valve portion. The vertical separation distance from the engaging portion of the valve body and the second lift amount are respectively set to a lift amount obtained by adding the predetermined amount to the first lift amount. Control valve for capacity compressor.