CN107606235B - Control valve structure and compressor with same - Google Patents

Abstract

The invention provides a control valve structure and a compressor with the same. The control valve structure comprises a valve body, wherein the valve body is provided with a containing cavity; the valve core is movably arranged in the accommodating cavity; the plunger is movably arranged in the accommodating cavity, and the valve core can drive the plunger to reciprocate along the axial direction of the accommodating cavity; and the valve core is movably connected with the plunger through the steering assembly. A steering assembly is disposed between the valve core and the plunger such that the valve core is movable relative to the plunger. The arrangement is such that when the spool moves or pushes the plunger in a lateral direction, when the friction between one of the spool or plunger and the chamber wall of the receiving chamber is excessive, one of the spool and plunger can be displaced relative to the other by a certain amount in the longitudinal direction to prevent the friction between the spool or plunger and the chamber wall from increasing further, thereby avoiding the situation that the spool and plunger are stuck. The control valve structure adopting the structure effectively improves the reliability and the practicability of the control valve.

Description

Control valve structure and compressor with same

Technical Field

The invention relates to the technical field of compressor equipment, in particular to a control valve structure and a compressor with the same.

Background

In an air conditioning system, in order to achieve the room temperature set by a user, a variable-frequency compressor technology is currently generally adopted, namely, a mode of realizing adjustable cooling capacity by controlling the rotating speed of a compressor is adopted, so that the aim of accurately controlling the room temperature is fulfilled. However, the minimum refrigerating capacity of the variable frequency compressor is still larger under certain environments due to the limitation of the minimum rotating speed of the compressor, so that a double-cylinder or multi-cylinder capacity-changing technology is provided in the compressor industry to control the refrigerating capacity of the compressor, and the minimum output of the refrigerating capacity of the compressor is further reduced, so that the aims of more accurate temperature control, energy conservation and consumption reduction are fulfilled. However, in the prior art, as shown in fig. 1, in the process of controlling the volume variation of the volume-variable cylinder by using the control valve 10', the valve core section a and the plunger section b are integrally provided, and thus the valve core of the control valve is easily jammed.

Disclosure of Invention

The invention mainly aims to provide a control valve structure and a compressor with the same, so as to solve the problem that a valve core in the prior art is easy to be blocked.

In order to achieve the above object, according to one aspect of the present invention, there is provided a control valve structure comprising: a valve body having a receiving chamber; the valve core is movably arranged in the accommodating cavity; the plunger is movably arranged in the accommodating cavity, and the valve core can drive the plunger to reciprocate along the axial direction of the accommodating cavity; and the valve core is movably connected with the plunger through the steering assembly.

Further, the spool and the plunger have a relatively collinear position when collinear with the axis extension of the spool and the axis extension of the plunger, and a relatively oblique position when the axis extension of the spool and the axis extension of the plunger have an included angle.

Further, the steering assembly includes: the first end of the first steering piece is connected with the valve core; and the first end of the second steering piece is connected with the plunger, and the second end of the second steering piece is connected with the first steering piece.

Further, the steering assembly further includes: the second end of the first steering member is connected with the steering knuckle, the second end of the first steering member rotates around the steering knuckle to rotate by a first preset angle along a first direction, the second end of the second steering member is connected with the steering knuckle, the second end of the second steering member rotates by a second preset angle along a second direction, an included angle is formed between the first direction and the second direction, and the second steering member is connected with the first steering member through the steering knuckle.

Further, the first preset angle and/or the second preset angle is beta, wherein beta is more than or equal to 0 and less than or equal to 180 degrees.

Further, the valve body includes: the plunger is movably arranged in the valve seat along the axial direction of the inner cavity of the valve seat; the valve core is movably arranged in the valve cover along the axial direction of the inner cavity of the valve cover, and an accommodating cavity is enclosed between the inner cavity of the valve seat and the inner cavity of the valve cover.

Further, the first end of the valve seat is connected with the valve cover, the first end of the valve seat is provided with a matching hole matched with the second steering member, a limiting step is arranged on the inner peripheral surface of the matching hole, the outer diameter of the first end of the second steering member is larger than the inner diameter of the limiting step, the end face of the first end of the second steering member is provided with a contact position propped against the table top of the limiting step, and the end face of the first end of the second steering member is provided with a separation position separated from the table top.

Further, the valve cover is provided with a connecting section which extends into the matching hole to be connected with the valve seat, the diameter of the matching hole is E1, the diameter of the outer peripheral surface of the connecting section is E2, the diameter of the inner cavity of the valve cover is E3, the valve core is directly E4, the length of the connecting section is L1, and the length of the inner cavity of the valve cover is L2, wherein (E1-E2) multiplied by L2/L1 is less than or equal to (E3-E4).

Further, a low-pressure channel and a high-pressure channel are formed in the side wall of the valve seat, the low-pressure channel and the high-pressure channel are arranged at intervals, the low-pressure channel and the high-pressure channel are communicated with the inner cavity of the valve seat, and a first depressurization groove is formed in the side wall, opposite to the low-pressure channel, of the inner cavity of the valve seat.

Further, the area of the cross section of the depressurization groove is the same as the area of the cross section of the low-pressure passage or the high-pressure passage.

Further, a second depressurization groove is formed in the side wall, opposite to the high-pressure channel, of the inner cavity of the valve seat.

Further, a variable-volume channel is arranged on the side wall of the valve seat, the variable-volume channel is positioned between the low-pressure channel and the high-pressure channel, and the variable-volume channel is communicated with the inner cavity of the valve seat.

Further, the plunger includes: the first end of the first composition section is connected with the steering assembly, and the outer peripheral surface of the first composition section is provided with a first annular groove; the first end of the second component section is connected with the second end of the first component section; the first end of the third composition section is connected with the second end of the second composition section, the outer peripheral surface of the third composition section is provided with a second annular groove, the outer diameters of the first composition section and the third composition section are the same, and the outer diameter of the second composition section is smaller than that of the first composition section and the third composition section, so that the third annular groove is formed between the outer peripheral surface of the second composition section and the first composition section and the third composition section.

Further, the valve core drives the plunger to move so that the plunger has a first position and a second position in the inner cavity of the valve seat, when the plunger is located at the first position, the low-pressure channel is communicated with the first annular groove and the first depressurization groove, the high-pressure channel and the variable-volume channel are communicated with the third annular groove and the second depressurization groove, and the side wall of the valve seat seals the second annular groove.

Further, when the plunger is located at the second position, the low-pressure channel and the variable-volume channel are communicated with the third annular groove and the first depressurization groove, the high-pressure channel is communicated with the second annular groove and the second depressurization groove, and the side wall of the valve seat seals the first annular groove.

According to another aspect of the present application, there is provided a compressor including a control valve structure, the control valve structure being the control valve structure described above.

By applying the technical scheme of the application, the steering assembly is arranged between the valve core and the plunger, so that the valve core can move relative to the plunger. The arrangement is such that when the spool moves or pushes the plunger in a lateral direction, when the friction between one of the spool or plunger and the chamber wall of the receiving chamber is excessive, one of the spool and plunger can be displaced relative to the other by a certain amount in the longitudinal direction to prevent the friction between the spool or plunger and the chamber wall from increasing further, thereby avoiding the situation that the spool and plunger are stuck. The control valve structure adopting the structure effectively improves the reliability and the practicability of the control valve.

Drawings

The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:

Fig. 1 shows a schematic construction of a compressor according to the prior art;

fig. 2 shows a schematic structural view of an embodiment of a compressor according to the present invention;

FIG. 3 shows a schematic structural view of an embodiment of a valve seat according to the present invention;

FIG. 4 shows a schematic cross-sectional view of the structure of FIG. 3 in the direction A-A;

FIG. 5 shows a schematic cross-sectional structure in the direction G-G of FIG. 4;

FIG. 6 shows a schematic cross-sectional structure in the H-H direction of FIG. 4;

FIG. 7 shows a schematic structural view of an embodiment of a valve cover according to the present invention;

FIG. 8 shows a schematic structural view of an embodiment of a knuckle according to the present invention;

fig. 9 is a schematic structural view showing an embodiment of a turning state of the first knuckle according to the present invention;

fig. 10 is a schematic structural view showing an embodiment of a turning state of a second knuckle according to the present invention;

FIG. 11 shows a schematic diagram of an exploded construction of an embodiment of a valve body structure according to the present invention;

FIGS. 12 and 13 are schematic structural views showing the forces to which the plunger is subjected when moving from the second position to the first position;

FIGS. 14 and 15 are schematic structural views showing the forces to which the plunger is subjected when moving from the first position to the second position;

FIG. 16 shows a schematic structural view of a valve spool, knuckle and plunger assembly according to the present invention;

Fig. 17 shows a schematic structural view of a cylinder according to the present application.

Wherein the above figures include the following reference numerals:

10', a valve core;

10. a valve seat; 11. a mating hole; 12. a limit step; 13. a low pressure passage; 14. a high pressure passage; 15. a first depressurization tank; 16. a variable capacitance channel; 17. a second depressurization tank;

20. a valve cover; 21. a connection section; 22. an electromagnetic coil; 23. a return spring;

30. a valve core;

40. a plunger; 41. a first component section; 42. a second component section; 43. a third component section;

50. a steering assembly; 51. a first steering member; 52. a knuckle; 53. a second steering member;

61. a first annular groove; 62. a second annular groove; 63. a third annular groove;

71. a housing; 72. a lower cover plate; 73. a sub-bearing; 74. a variable volume cylinder; 741. a slide groove; 742. a communication passage; 743. an air suction port;

75. a partition plate; 76. a first cylinder; 77. a main bearing; 78. a crankshaft; 79. a stator;

80. a rotor; 81. a knockout; 82. a first roller; 83. a first slide; 84. a variable-capacitance roller; 85. a variable capacity slide sheet; 86. a variable capacitance control cavity; 87. a pin; 88. a pin spring; 89. a clamping groove.

Detailed Description

It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.

It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.

It should be noted that the terms "first," "second," and the like in the description and the claims and drawings of the present application are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the terms so used are interchangeable under appropriate circumstances such that the embodiments of the application described herein are, for example, capable of operation in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.

Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.

Exemplary embodiments according to the present application will now be described in more detail with reference to the accompanying drawings. These exemplary embodiments may, however, be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. It should be understood that these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of these exemplary embodiments to those skilled in the art, that in the drawings, it is possible to enlarge the thicknesses of layers and regions for clarity, and that identical reference numerals are used to designate identical devices, and thus descriptions thereof will be omitted.

As shown in connection with fig. 2 to 17, a control valve structure is provided according to an embodiment of the present invention.

The control valve structure includes a valve body, a spool 30, a plunger 40, and a steering assembly 50. The valve body has a receiving chamber in which the valve cartridge 30 is movably disposed. The plunger 40 is movably disposed in the accommodating cavity, and the valve core 30 can drive the plunger 40 to reciprocate along the axial direction of the accommodating cavity. The valve spool 30 is movably coupled to the plunger 40 by a steering assembly 50.

In this embodiment, a steering assembly is provided between the valve spool and the plunger such that the valve spool is movable relative to the plunger. The arrangement is such that when the spool moves or pushes the plunger in a lateral direction, when the friction between one of the spool or plunger and the chamber wall of the receiving chamber is excessive, one of the spool and plunger can be displaced relative to the other by a certain amount in the longitudinal direction to prevent the friction between the spool or plunger and the chamber wall from increasing further, thereby avoiding the situation that the spool and plunger are stuck. The control valve structure adopting the structure effectively improves the reliability and the practicability of the control valve.

Wherein the spool 30 and the plunger 40 have a relatively collinear position when collinear with the axis extension of the spool 30 and the axis extension of the plunger 40, and a relatively inclined position when the axis extension of the spool 30 and the axis extension of the plunger 40 have an included angle. The arrangement is such that when one of the valve core 30 and the plunger 40 is in contact with the wall of the accommodation chamber and is about to seize, the other can be changed by tilting, i.e. such that the valve core and the plunger can adjust their own movement state by adjusting their own position, to prevent the valve core and the plunger from seizing.

Specifically, as shown in fig. 8 to 11, the steering assembly 50 includes a first steering member 51 and a second steering member 53. The first end of the first steering member 51 is connected to the spool 30. The first end of the second turn member 53 is connected to the plunger 40 and the second end of the second turn member 53 is connected to the first turn member 51. The steering assembly is simple in structure and convenient to operate.

Preferably, the steering assembly 50 is further provided with a knuckle 52 in order to further improve the reliability of the knuckle. The second end of the first steering member 51 is connected to the knuckle 52, the second end of the first steering member 51 is rotatable around the knuckle 52 in a first direction by a first predetermined angle, the second end of the second steering member 53 is connected to the knuckle 52, the second end of the second steering member 53 is rotatable in a second direction by a second predetermined angle, the first direction has an angle with the second direction, and the second steering member 53 is connected to the first steering member 51 via the knuckle 52. As shown in fig. 8, the first direction may be an X-axis direction in the drawing, and the second direction may be a Y-axis direction in the drawing, wherein the X-axis is orthogonal to the Y-axis, and as shown in fig. 9, the first preset angle is β,0 Σ, and 180 °. Of course, the second preset angle may be set to be equal to the first preset angle.

As shown in fig. 2 to 7, the valve body includes a valve seat 10 and a valve cover 20. The plunger 40 is movably disposed in the valve seat 10 in the axial direction of the inner cavity of the valve seat 10. The valve cover 20 is connected with the valve seat 10, the valve core 30 is movably arranged in the valve cover 20 along the axial direction of the inner cavity of the valve cover 20, and an accommodating cavity is enclosed between the inner cavity of the valve seat 10 and the inner cavity of the valve cover 20. The first end of the valve seat 10 is connected with the valve cover 20, the first end of the valve seat 10 is provided with a matching hole 11 matched with the second steering member 53, the inner circumferential surface of the matching hole 11 is provided with a limiting step 12, the outer diameter of the first end of the second steering member 53 is larger than the inner diameter of the limiting step 12, the end face of the first end of the second steering member 53 is provided with a contact position propped against the table top of the limiting step 12, and the end face of the first end of the second steering member 53 is provided with a separation position separated from the table top. The arrangement can improve the reliability and the practicability of the valve body structure.

Further, as shown in fig. 4, 7 and 12, the valve cap 20 has a connecting section 21, the connecting section 21 extends into the fitting hole 11 to be connected with the valve seat 10, the diameter of the fitting hole 11 is E1, the diameter of the outer peripheral surface of the connecting section 21 is E2, the diameter of the inner cavity of the valve cap 20 is E3, the direct of the valve core 30 is E4, the length of the connecting section 21 is L1, and the length of the inner cavity of the valve cap 20 is L2, wherein E1-E2×l2/L1 is less than or equal to E3-E4. This arrangement can further improve the reliability and practicality of the valve body structure.

As shown in fig. 11 to 15, a low-pressure channel 13 and a high-pressure channel 14 are formed on the side wall of the valve seat 10, the low-pressure channel 13 and the high-pressure channel 14 are arranged at intervals, the low-pressure channel 13 and the high-pressure channel 14 are communicated with the inner cavity of the valve seat 10, and a first depressurization groove 15 is formed on the side wall, opposite to the low-pressure channel 13, of the inner cavity of the valve seat 10. By the arrangement, the valve core and the plunger slide more smoothly, and the reliability and stability of the valve body structure are improved.

Preferably, the area of the cross section of the depressurization groove 15 is the same as the area of the cross section of the low pressure passage 13 or the high pressure passage 14. The arrangement can balance the stress of the plunger, and the stability of the plunger is improved.

Further, a second depressurization groove 17 is provided in a side wall of the inner cavity of the valve seat 10 opposite to the high-pressure passage 14. The arrangement can also play a role in balancing the stress of the plunger, so that the stability of the plunger is improved.

The side wall of the valve seat 10 is also provided with a variable volume passage 16. The variable volume passage 16 is located between the low pressure passage 13 and the high pressure passage 14, and the variable volume passage 16 communicates with the inner chamber of the valve seat 10. This arrangement improves the practicality and reliability of the valve body structure.

Specifically, as shown in fig. 16, the plunger 40 includes a first constituent segment 41, a second constituent segment 42, and a third constituent segment 43. The first end of the first constituent segment 41 is connected to the steering assembly 50, and the outer peripheral surface of the first constituent segment 41 is provided with a first annular groove 61. The first end of the second component section 42 is connected to the second end of the first component section 41. The first end of the third component section 43 is connected with the second end of the second component section 42, the outer peripheral surface of the third component section 43 is provided with a second annular groove 62, the outer diameters of the first component section 41 and the third component section 43 are the same, and the outer diameter of the second component section 42 is smaller than the outer diameters of the first component section 41 and the third component section 43, so that a third annular groove 63 is formed between the outer peripheral surface of the second component section 42 and the first component section 41 and the third component section 43. This arrangement can improve the reliability and practicality of the plunger.

The valve core 30 moves the plunger 40 such that the plunger 40 has a first position and a second position within the interior cavity of the valve seat 10. As shown in fig. 13 and 14, when the plunger 40 is in the first position, the low pressure passage 13 communicates with the first annular groove 61, the first depressurization groove 15. The high-pressure passage 14 and the variable-volume passage 16 are communicated with the third annular groove 63 and the second depressurization groove 17, and the second annular groove 62 is sealed by the side wall of the valve seat 10. As shown in fig. 15 and 16, when the plunger 40 is in the second position, the low-pressure passage 13, the variable-volume passage 16, and the third annular groove 63, the first depressurization groove 15 are in communication. The high pressure passage 14 communicates with the second annular groove 62, the second depressurization groove 17, and the side wall of the valve seat 10 seals the first annular groove 61. This arrangement can improve the sealability and reliability of the valve body structure.

The valve body structure can also be used in the technical field of compressor equipment, namely, according to another aspect of the invention, a compressor is provided. The compressor includes a control valve structure, which is the control valve structure in the above embodiment. The control valve structure includes a valve body, a spool 30, a plunger 40, and a steering assembly 50. The valve body has a receiving chamber in which the valve cartridge 30 is movably disposed. The plunger 40 is movably disposed in the accommodating cavity, and the valve core 30 can drive the plunger 40 to reciprocate along the axial direction of the accommodating cavity. The valve spool 30 is movably coupled to the plunger 40 by a steering assembly 50.

In this embodiment, a steering assembly is provided between the valve spool and the plunger such that the valve spool is movable relative to the plunger. The arrangement is such that when the spool moves or pushes the plunger in a lateral direction, when the friction between one of the spool or plunger and the chamber wall of the receiving chamber is excessive, one of the spool and plunger can be displaced relative to the other by a certain amount in the longitudinal direction to prevent the friction between the spool or plunger and the chamber wall from increasing further, thereby avoiding the situation that the spool and plunger are stuck. The control valve structure adopting the structure effectively improves the reliability and the practicability of the compressor.

Specifically, in the prior art, when the sliding block is overlong, the valve body is extremely easy to contact with the sliding block to cause the increase of resistance in the sliding block movement process, even the sliding block is blocked, so that the compressor cannot complete the normal mode conversion process, the reliability of the compressor is reduced, and the valve body structure of the application avoids the sliding block blocking caused by the contact of the sliding block and the valve body, reduces the resistance of the sliding block in the reciprocating sliding process, and improves the reliability of the compressor in conversion between different modes. Meanwhile, the assembly difficulty of the compressor is reduced, and the assembly manufacturability of the compressor is improved.

The compressor comprises a liquid separator 81, a housing 71, a motor comprising a stator 79 and a rotor 80, a pump body assembly, a pressure conversion assembly. The motor and pump body assembly are arranged in the shell 71, the pump body assembly is arranged at the lower part of the motor, and the motor is connected with the pump body assembly through the crankshaft 78 and drives the crankshaft 78 to rotate so as to compress the gas sucked into the cylinder. The pump body assembly having a plurality of cylinders and having at least one variable volume cylinder 74, the pump body assembly further comprising a main bearing 77, a first cylinder 76, a first slide 83, a first roller 82, a variable volume cylinder 74, a variable volume slide 85, a variable volume roller 84, a diaphragm 75, a secondary bearing 73, a lower cover plate 72, a pin 87, a pin spring 88; the variable-volume cylinder 74 is provided with a variable-volume roller 84 and a variable-volume slide 85 arranged in a slide groove 741 of the variable-volume cylinder, the tail part of the variable-volume slide is enclosed into a sealed variable-volume control cavity by a baffle plate, the variable-volume cylinder and a secondary bearing, and the head part of the variable-volume slide is close to the central shaft of the variable-volume cylinder. The pressure conversion assembly comprises a valve seat, a valve cover, a solenoid 22, a reciprocating motion assembly and a return spring 23, wherein the valve seat is arranged on the side, far away from the auxiliary bearing, of the lower cover plate and is clung to the lower cover plate, the valve cover is provided with a connecting part matched with the valve seat and extends to the outside of the compressor through the shell of the compressor, the valve cover is a cylindrical member, the solenoid 22, the reciprocating motion assembly and the return spring 23 are sleeved on the cylindrical member extending to the outside of the shell, and air tightness is arranged between the cylindrical member and the shell so as to isolate the external environment of the shell from the inside of the shell. The electromagnetic coil on the pressure conversion assembly is controlled to be electrified and powered off, the reciprocating assembly is controlled to move left or right, low-pressure or high-pressure gas is selectively led into the variable-volume control cavity, and the head of the variable-volume sliding vane is separated from or clung to the variable-volume roller, so that the variable-volume cylinder selectively idles or works.

The reciprocating motion assembly comprises a valve core, a steering assembly and a plunger. The valve core is arranged in the cylinder component and is used for pulling or pushing the valve core and the components thereof to move left or right under the attraction of electromagnetic force or the elasticity of the return spring, and the plunger is arranged in the piston hole in the valve seat and is used for selectively introducing low-pressure or high-pressure gas into the variable-volume control cavity. The steering assembly comprises a first steering member, a steering knuckle and a second steering member. The second steering member and the first steering member are rotatable about the Y-axis and the X-axis independently of each other with respect to the knuckle. The valve core can be connected with the second steering piece or the first steering piece at will, and the other end of the steering assembly is connected with the plunger. Wherein, the materials of the cylinder component, the return spring, the plunger, the valve seat and the steering component have no magnetism, and the materials of the valve core have magnetism conductivity.

A limiting surface is formed between the end part of the second steering piece and the plunger, and the limiting surface is used for limiting the moving distance of the reciprocating motion assembly under the action of the elastic force of the return spring when being attached to a limiting step on the valve seat.

The compressor further comprises a pin 87 and a pin spring 88 which are arranged in the auxiliary bearing and are positioned right below the variable capacity sliding sheet, wherein the pin is communicated with the variable capacity control cavity 86 close to the side of the variable capacity cylinder, and the pin is provided with the pin spring close to the side of the lower cover plate and is communicated with an air suction port 743 of the variable capacity cylinder and a low-pressure channel on the valve seat.

The reciprocating movement assembly moves rightwards under the action of the restoring spring force until the limiting step and the end part of the second steering piece are mutually attached, and the continuous movement of the reciprocating movement assembly is prevented, at the moment, the low-pressure channel and the variable-volume channel are changed from being communicated to be closed, the variable-volume channel and the high-pressure channel are changed from being closed to be communicated, and the first annular groove 61 changes the first depressurization groove 15 and the low-pressure channel from being closed to be communicated. The reciprocating assembly moves leftward under the action of electromagnetic force until the valve core hole of the cylindrical member is kept away from the valve seat side to prevent continued movement thereof, at which time the high-pressure passage and the variable-volume passage are changed from closed to open and the variable-volume passage and the low-pressure passage are changed from closed to open, and the second annular groove 62 changes the second depressurization groove 17 and the high-pressure passage from closed to open. Wherein the positions between the low pressure passage and the high pressure passage are interchangeable.

The pin is arranged in the auxiliary bearing and is positioned under the variable-capacity sliding sheet, a channel for arranging the pin is communicated with the variable-capacity control cavity, a low-pressure channel close to the side of the lower cover plate and the valve seat, an air suction port 743 of the variable-capacity cylinder are mutually communicated, a pin spring is arranged on the side of the low-pressure channel, the pressure conversion component is arranged on the lower cover plate far away from the side of the auxiliary bearing, and a communication channel 742 is further arranged on the variable-capacity cylinder.

The valve seat is located the laminating that the auxiliary bearing side has the gas tightness with the lower apron is kept away from to the lower apron, is provided with low pressure channel, high pressure channel, varactor passageway, plunger hole, mating hole on the valve seat, first depressurization groove 15, second depressurization groove 17. The central axis of the plunger hole runs through the valve seat along the normal plane direction of the axial direction of the crankshaft, the other end of the plunger hole is provided with a matching hole, the central axis of the matching hole is coaxial with the central axis of the plunger hole, the other end of the matching hole runs through the valve seat, a limit step is naturally formed between the matching hole and the plunger hole due to diameter difference, the matching hole is mainly used for matching with the connecting part of the cylindrical member and limiting deflection of the cylindrical member, a low-pressure channel, a variable-volume channel and a high-pressure channel are sequentially arranged in the normal direction of the plunger hole, and the low-pressure channel and the high-pressure channel are positioned at two sides of the variable-volume channel. The low pressure channel, the variable-volume channel and the high pressure channel all penetrate through the first side interface of the plunger hole and are communicated with the plunger hole, a first depressurization groove 15 is arranged along the direction of the low pressure channel, the central axis of the first depressurization groove 15 is coaxial with the low pressure channel, and the cross section area of the first depressurization groove is equal to the cross section area of the low pressure channel; a second depressurization groove 17 is arranged along the direction of the high-pressure channel, the central axis of the second depressurization groove 17 is coaxial with the high-pressure channel, and the sectional area of the second depressurization groove is equal to the sectional area of the high-pressure channel; the low pressure channel is communicated with the air suction port of the air cylinder and the side of the pin close to the lower cover plate, the pressure of the low pressure channel, the air suction port of the air cylinder and the side of the pin close to the lower cover plate are equal to the suction pressure, the high pressure channel is communicated with the channel for discharging air flow of the variable capacity air cylinder, the pressure of the high pressure channel is equal to the discharge pressure, the variable capacity channel is communicated with the variable capacity control cavity at the tail part of the variable capacity sliding sheet, and the pressure of the variable capacity channel is equal to the pressure of the variable capacity control cavity.

Further, the area of the cross section of the low pressure passage refers to the projected area of the intersecting curved surface of the low pressure passage and the plunger hole along the normal direction of the axis of the plunger Kong Zhongxian, the area of the cross section of the first pressure reducing groove 15 refers to the projected area of the intersecting curved surface of the first pressure reducing groove 15 and the plunger hole along the normal direction of the axis of the plunger Kong Zhongxian, the area of the cross section of the high pressure passage refers to the projected area of the intersecting curved surface of the high pressure passage and the plunger hole along the normal direction of the axis of the plunger Kong Zhongxian, and the sectional area of the second pressure reducing groove 17 refers to the projected area of the intersecting curved surface of the second pressure reducing groove 17 and the plunger hole along the normal direction of the axis of the plunger Kong Zhongxian.

The cylindrical member has a connecting portion which is fitted to the valve seat and extends from the inside of the housing to the outside of the housing, the cylindrical member and the housing are airtight, the outside environment of the housing is isolated from the inside of the housing by high pressure, and a valve element hole having one end open and one end closed is provided on the side of the cylindrical member close to the inside of the housing.

A reciprocating motion assembly: the valve core is arranged in a valve core hole of the cylindrical member, the plunger is arranged in a plunger hole in the valve seat, and the steering assembly is used for connecting the valve core and the plunger into a whole. The valve body is provided in the cylindrical member, and a spring hole for mounting a return spring is provided in the valve body on the side of the valve body Kong Mangkong of the cylindrical member.

The plunger is provided with a first cylindrical surface, a second cylindrical surface, and a third annular groove 63. The first cylindrical surface is positioned close to the steering assembly side, the first cylindrical surface is provided with a first annular groove 61, the second cylindrical surface is positioned far away from the steering assembly side, the second cylindrical surface is provided with a second annular groove 62, the diameters of the first cylindrical surface and the second cylindrical surface are equal, and a third annular groove 63 is arranged between the first cylindrical surface and the second cylindrical surface. The first annular groove 61 is used for communicating the low-pressure channel with the first depressurization groove 15 and making the pressure equal, the second annular groove 62 is used for communicating the high-pressure channel with the second depressurization groove 17 and making the pressure equal, and the third annular groove 63 is used for selectively communicating the low-pressure channel with the variable-volume channel or the variable-volume channel with the high-pressure channel.

In this embodiment, the steering assembly is composed of a second steering member, a first steering member and a steering knuckle, the second steering member is connected with the valve core (or the plunger), the first steering member is connected with the plunger (or the valve core), the second steering member and the first steering member are connected by the steering knuckle, the second steering member can drive the valve core (or the plunger) to rotate around the steering knuckle by plus or minus 90 degrees along the Y axis, and the first steering member can drive the plunger (or the valve core) to rotate around the steering knuckle by plus or minus 90 degrees along the X axis. The second steering member (or the first steering member) and the plunger form a limiting surface due to the diameter difference, and the limiting surface is attached to a limiting step on the valve seat to prevent the reciprocating movement assembly from moving towards the direction approaching the valve seat. The return spring is arranged between the valve core hole of the cylinder component and the spring hole of the valve core and provides elastic force for the valve core, so that the reciprocating motion assembly has a motion trend close to the valve seat. The electromagnetic coil is sleeved on a cylindrical member extending to the outside of the shell and has two states of power on and power off, when the electromagnetic coil is powered on, the electromagnetic force generated by the electromagnetic induction principle attracts the valve core with magnetic conductivity and drives the valve core and components thereof to move away from the valve seat, when the electromagnetic coil is powered off, the electromagnetic force disappears, and the valve core and the components thereof move towards the direction close to the valve seat under the action of the restoring spring force.

The working and idling conversion principle of the variable volume cylinder is as follows: when the electromagnetic coil is electrified, the electromagnetic force F6 generated by the electromagnetic coil attracts the valve core and the components thereof to move away from the valve seat, and the valve core and the components thereof are not moved any more due to the blocking of the side of the valve core Kong Mangkong of the cylindrical member, the variable-volume passage and the low-pressure passage are conducted through the third annular groove 63 arranged on the plunger and disconnected from the high-pressure passage, low-pressure gas is guided to the variable-volume control cavity through the passage, at the moment, the tail part of the variable-volume sliding vane, the pin is close to the side of the variable-volume cylinder, the side of the pin close to the lower cover plate is low-pressure, the side of the variable-volume sliding vane is close to the inner circle of the cylinder is low-pressure, and the pin moves towards the side close to the variable-volume sliding vane under the action of the pin spring and is inserted into the clamping groove 89 on the variable-volume sliding vane, so that the variable-volume sliding vane is separated from the variable-volume roller, and even if the crankshaft rotates the variable-volume cylinder is not in the air suction, compression and exhaust processes any more and is in an idle state. When the electromagnetic coil is powered off, electromagnetic force disappears, the valve core moves towards the direction close to the valve seat under the action of restoring spring force F5 until the limiting step is attached to the limiting surface to stop moving, the variable-volume channel and the high-pressure channel are communicated with each other through the third annular groove 63 and disconnected with the low-pressure channel, high-pressure gas is introduced into the variable-volume control cavity at the tail part of the variable-volume sliding vane through the third annular groove 63 and the variable-volume channel, at the moment, the side pressure of the tail part of the variable-volume sliding vane and the pin close to the variable-volume cylinder is high pressure, the side pressure of the variable-volume sliding vane close to the center side of the variable-volume cylinder is low pressure, the pin moves towards the side close to the lower cover plate against the spring force of the pin under the action of gas force and is separated from the variable-volume sliding vane, and the variable-volume sliding vane moves towards the center of the variable-volume cylinder under the action of the gas force until the variable-volume sliding vane is abutted against the variable-volume roller, at the moment, the variable-volume sliding cylinder enters into a working state under the driving of the crankshaft, and the variable-volume cylinder is subjected to air suction, compression and air exhaust.

Action of the steering assembly: when the constraint action of the valve seat matching hole on the cylindrical member in the normal direction along the central axis of the plunger hole is insufficient, the cylindrical member connecting part deflects slightly relative to the valve seat matching hole, so that the blind hole on the blind hole side of the valve core hole of the cylindrical member deflects and amplifies relative to the central axis of the plunger, the valve core is possibly contacted with the side wall of the valve core hole of the cylindrical member, and if the valve core and the plunger are arranged into an integral structure, the part is blocked in the valve core hole and cannot move, so that the variable-volume cylinder cannot finish the conversion of idle running and working two states. If the parts are changed into reciprocating motion components, the valve core can rotate along the X axis and Y axis directions relative to the plunger, even if the cylindrical component deflects to a certain extent relative to the central axis of the plunger hole, the reciprocating motion components still can move under the action of electromagnetic force F6 or restoring spring force F5, and the structure improves the reliability of the variable volume cylinder in the conversion of two states of idling and working and can reduce the assembly difficulty of the compressor; to further reduce the likelihood of the valve spool coming into contact with the side wall of the spool bore of the cylindrical member, it can be controlled by the following relationship: (E1-E2) L2/L1 is less than or equal to (E3-E4), wherein E2 is the diameter of the connecting part of the cylinder component, E1 is the diameter of the matching hole of the valve seat, L1 is the length of the connecting part of the cylinder component, L2 is the length of the valve core hole on the cylinder component, E3 is the diameter of the valve core hole, and E4 is the diameter of the valve core; L2/L1 is an enlargement factor of the cylindrical member on the side of the cylindrical member valve core Kong Mangkong after the cylindrical member connecting portion is deflected with respect to the plunger hole, and L3 is the length of the plunger hole of the valve seat as shown in fig. 4.

The first depressurization groove 15 and the second depressurization groove 17 function: when the low pressure channel is communicated with the variable volume channel, a force F1 along the normal direction of the central axis of the plunger hole is generated due to the communication of the high pressure channel and the plunger hole, and the force F1 acts on the plunger to generate a friction force on the plunger along the axial direction of the plunger hole, when the electromagnetic force disappears, the valve core and the components thereof can move after overcoming the friction force under the action of the restoring spring force F5, and at the moment, the valve core and the components thereof can move controllably only by setting a larger restoring spring force F5; when the high-pressure channel is communicated with the variable-volume channel, a force F3 along the normal direction of the central axis of the plunger hole is generated due to the communication of the low-pressure channel and the plunger hole, and the force F3 acts on the plunger to generate a friction force on the plunger along the axial direction of the plunger hole, when the electromagnetic force F6 is generated, the valve core and the components thereof can move after overcoming the friction force under the action of the electromagnetic force F6, and when the working condition is severe, the valve core and the components thereof can move controllably only by setting a larger electromagnetic force F6; the increase of the return spring force F5 and the electromagnetic force F6 not only increases the power consumption of the electromagnetic coil, but also reduces the reliability of the switching of the varactor cylinder in both modes. If the plunger hole is provided with the first depressurization groove 15 and the second depressurization groove 17 respectively, the stopper is provided with the first annular groove 61 and the second annular groove 62, when the variable-volume cylinder needs to be changed from idling to working, the high-pressure channel is communicated with the second depressurization groove 17 through the second annular groove 62, the high-pressure channel and the second depressurization groove 17 can generate two opposite forces F1 and F2 to be applied to the plunger, if the sectional areas of the high-pressure channel and the second depressurization groove 17 are equal, the resultant force of F1 and F2 borne by the plunger is 0 newton, the friction force borne by the plunger is greatly reduced, and at the moment, the restoring spring force can push the valve core and the components thereof to move only by providing smaller force. When the variable-capacity cylinder needs to be changed into idle operation, the low-pressure channel is communicated with the first pressure reducing groove 15 through the first annular groove 61, the low-pressure channel and the first pressure reducing groove 15 can generate two opposite forces F3 and F4 to be applied to the plunger, if the sectional areas of the low-pressure channel and the first pressure reducing groove 15 are equal, the resultant force of F3 and F4 borne by the plunger is 0 newton, the friction force borne by the plunger is greatly reduced, and at the moment, the electromagnetic coil can attract the valve core and the components thereof to move only by providing a small force.

Selection of cylinder member, return spring, plunger, valve seat, steering assembly, valve core material: the variable-volume cylinder can realize the conversion between idle running and working states by controlling the movement of the reciprocating motion assembly through electromagnetic force, and the smaller the loss of the electromagnetic force is, the higher the reliability of the conversion between the two states of the variable-volume cylinder is, so that the property of related parts is required, the cylinder component, the valve seat steering assembly and the plunger are required to have non-magnetic property so as to reduce the electromagnetic loss, and the valve core is required to have stronger magnetic permeability, namely attractive force is generated when an electrified electromagnetic coil or magnet is close to the valve core. For the return spring, even if the return spring has magnetism conductivity and has small electromagnetic loss, the return spring can deflect along the radial direction of the valve core hole under the action of electromagnetic force to influence the return spring to smoothly enter the valve core hole on the valve core, so the return spring also needs to have non-magnetic property.

In addition to the foregoing, references in the specification to "one embodiment," "another embodiment," "an embodiment," etc., indicate that the particular feature, structure, or characteristic described in connection with the embodiment is included in at least one embodiment of the application, as generally described. The appearances of the phrase in various places in the specification are not necessarily all referring to the same embodiment. Further, when a particular feature, structure, or characteristic is described in connection with any embodiment, it is intended that such feature, structure, or characteristic be implemented within the scope of the application.

In the foregoing embodiments, the descriptions of the embodiments are emphasized, and for parts of one embodiment that are not described in detail, reference may be made to related descriptions of other embodiments.

The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (14)

1. A control valve structure, comprising:

a valve body having a receiving cavity;

a valve core (30), wherein the valve core (30) is movably arranged in the accommodating cavity;

the plunger (40) is movably arranged in the accommodating cavity, and the valve core (30) can drive the plunger (40) to reciprocate along the axial direction of the accommodating cavity;

-a steering assembly (50), the valve cartridge (30) being movably connected to the plunger (40) by means of the steering assembly (50);

the steering assembly (50) includes:

a first steering member (51), a first end of the first steering member (51) being connected to the spool (30);

-a second steering member (53), a first end of the second steering member (53) being connected to the plunger (40), a second end of the second steering member (53) being connected to the first steering member (51);

The steering assembly (50) further comprises:

the steering device comprises a steering knuckle (52), wherein the second end of a first steering member (51) is connected with the steering knuckle (52), the second end of the first steering member (51) is rotatable around the steering knuckle (52) along a first direction by a first preset angle, the second end of a second steering member (53) is connected with the steering knuckle (52), the second end of the second steering member (53) is rotatable along a second direction by a second preset angle, the first direction and the second direction have an included angle, and the second steering member (53) is connected with the first steering member (51) through the steering knuckle (52).

2. The control valve structure according to claim 1, characterized in that the spool (30) and the plunger (40) have a relative collinear position when collinear with an axis extension of the spool (30) and an axis extension of the plunger (40), and a relative inclined position when an axis extension of the spool (30) and an axis extension of the plunger (40) have an included angle.

3. The control valve structure of claim 1, wherein the first predetermined angle and/or the second predetermined angle is β, wherein 0 β 180 °.

4. The control valve structure of claim 1, wherein said valve body comprises:

A valve seat (10), wherein the plunger (40) is movably arranged in the valve seat (10) along the axial direction of the inner cavity of the valve seat (10);

the valve cover (20), valve cover (20) with disk seat (10) are connected, case (30) follow the axial of the inner chamber of valve cover (20) movably set up in valve cover (20), enclose between the inner chamber of disk seat (10) with the inner chamber of valve cover (20) is established into hold the chamber.

5. The control valve structure according to claim 4, characterized in that a first end of the valve seat (10) is connected with the valve cover (20), the first end of the valve seat (10) is provided with a fitting hole (11) that fits with the second turning member (53), a limit step (12) is provided on an inner peripheral surface of the fitting hole (11), an outer diameter of the first end of the second turning member (53) is larger than an inner diameter of the limit step (12), an end face of the first end of the second turning member (53) has a contact position that abuts against a mesa of the limit step (12), and an end face of the first end of the second turning member (53) has a release position that releases from the mesa.

6. The control valve structure according to claim 5, characterized in that the valve cover (20) has a connecting section (21), the connecting section (21) extends into the fitting hole (11) to be connected with the valve seat (10), the diameter of the fitting hole (11) is E1, the diameter of the outer peripheral surface of the connecting section (21) is E2, the diameter of the inner cavity of the valve cover (20) is E3, the direct of the valve element (30) is E4, the length of the connecting section (21) is L1, the length of the inner cavity of the valve cover (20) is L2, wherein (E1-E2) ×l2/l1 is + (E3-E4).

7. The control valve structure according to claim 4, wherein a low-pressure channel (13) and a high-pressure channel (14) are formed in a side wall of the valve seat (10), the low-pressure channel (13) and the high-pressure channel (14) are arranged at intervals, the low-pressure channel (13) and the high-pressure channel (14) are communicated with an inner cavity of the valve seat (10), and a first depressurization groove (15) is formed in a side wall, opposite to the low-pressure channel (13), of the inner cavity of the valve seat (10).

8. Control valve structure according to claim 7, characterized in that the area of the cross section of the depressurization groove (15) is the same as the area of the cross section of the low pressure channel (13) or the high pressure channel (14).

9. The control valve structure according to claim 7, characterized in that a second depressurization groove (17) is provided in a side wall of the inner cavity of the valve seat (10) opposite to the high-pressure passage (14).

10. The control valve structure according to claim 9, characterized in that a variable-volume channel (16) is further formed on the side wall of the valve seat (10), the variable-volume channel (16) is located between the low-pressure channel (13) and the high-pressure channel (14), and the variable-volume channel (16) is communicated with the inner cavity of the valve seat (10).

11. The control valve structure according to claim 10, characterized in that the plunger (40) comprises:

a first component section (41), wherein a first end of the first component section (41) is connected with the steering assembly (50), and a first annular groove (61) is formed in the peripheral surface of the first component section (41);

-a second component section (42), a first end of the second component section (42) being connected to a second end of the first component section (41);

the first end of the third composition section (43) is connected with the second end of the second composition section (42), a second annular groove (62) is formed in the outer peripheral surface of the third composition section (43), the outer diameters of the first composition section (41) and the third composition section (43) are the same, and the outer diameter of the second composition section (42) is smaller than the outer diameters of the first composition section (41) and the third composition section (43), so that a third annular groove (63) is formed between the outer peripheral surface of the second composition section (42) and the first composition section (41) and the third composition section (43).

12. The control valve structure according to claim 11, characterized in that the spool (30) moves the plunger (40) so that the plunger (40) has a first position and a second position in the inner cavity of the valve seat (10), the low pressure passage (13) communicates with the first annular groove (61) and the first depressurization groove (15) when the plunger (40) is located at the first position, the high pressure passage (14) and the variable volume passage (16) communicate with the third annular groove (63) and the second depressurization groove (17), and the side wall of the valve seat (10) seals the second annular groove (62).

13. The control valve structure according to claim 12, characterized in that when the plunger (40) is in the second position, the low pressure passage (13), the variable volume passage (16) are in communication with the third annular groove (63), the first depressurization groove (15), the high pressure passage (14) is in communication with the second annular groove (62), the second depressurization groove (17), and the side wall of the valve seat (10) seals the first annular groove (61).

14. A compressor comprising a control valve structure, characterized in that the control valve structure is the control valve structure of any one of claims 1 to 13.