JP2006183802A - Flow passage switching valve, compressor with flow passage switching valve and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve reliability of switching action by providing a compressor with a flow passage switching valve which is appropriate to be used for an on-vehicle air conditioner. <P>SOLUTION: A housing is attached to a compression part of a compressor main body. A valve chamber and ports are formed in the housing by cutting the housing. A continuity passage 31 is formed at a low pressure continuity part 3B of a main valve 3 provided in the valve chamber. A pressure equalizing hole 34 for communicating with the continuity passage 31 is formed at an auxiliary valve seat 33 of the main valve 3. A projection 35 is formed around the auxiliary valve seat 33. A pressure equalizing groove 42 in an arc shape forming a predetermined angle is formed at an auxiliary valve 4. Projections 43 are formed at two positioned on a back side of the auxiliary valve 4. A clutch mechanism is structured by the projections 35, 42. The pressure equalizing hole 34 is opened and closed by rotating the auxiliary valve 4. The main valve 3 is rotated via the clutch mechanism in a state that the continuity passage 31 and a pressure control space at upper part of the main valve 3 by opening the pressure equalizing hole 34. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a flow path switching valve used in a refrigeration cycle of an air conditioner, a compressor with a flow path switching valve having the flow path switching valve, and an air conditioner having the compressor with the flow path switching valve.

  Conventionally, this type of flow path switching valve is disclosed in, for example, Japanese Patent Laid-Open No. 9-292050. The flow path switching valve can obtain a seal pressure that presses the main valve against the valve seat by a differential pressure between the refrigerant pressure in the valve chamber and the refrigerant pressure in the conduction path of the main valve, and the seal structure can be simplified. However, this conventional flow path switching valve equalizes the pressure in the conduction path by the pilot valve and rotates the main valve with an indirect force that is the same as the magnetic force that drives the pilot valve. It is necessary to take time and timing when the main valve rotates, and the main valve may not rotate well.

On the other hand, a flow path switching valve that equalizes a conduction path using a sub valve and a pressure equalizing hole and transmits the driving force of the sub valve to the main valve to rotate the main valve is disclosed in, for example, Japanese Patent Application Laid-Open No. 2003-2003. This is disclosed in Japanese Patent No. 314715.
JP-A-9-292050 JP 2003-314715 A

  However, even in the flow path switching valve disclosed in Japanese Patent Application Laid-Open No. 2003-314715, the pressure equalization hole formed in the low pressure communication recess and the communication hole formed in the high pressure communication recess are formed by two closing valves corresponding to the sub valves. Each is opened and closed. Further, the closing valve support that moves the closing valve is rotated by a gear, and the main valve is rotated by the closing valve support and the interlocking protrusion provided on the main valve. Therefore, the structure becomes complicated, which becomes an obstacle for obtaining reliable operation.

  The present invention has been made in view of the above circumstances, and provides a highly reliable flow path switching valve, a compressor with a flow path switching valve, and an air conditioner that can smoothly operate with a simple configuration. Let it be an issue.

  The flow path switching valve according to claim 1 houses a main valve in a cylindrical valve chamber so as to be rotatable about an axis of the valve chamber, and a low pressure port and two switching ports in a valve seat facing the main valve. And the main valve is rotated so that the high pressure port is communicated with the other switching port, and the two switching is performed so that the low pressure port is communicated with the one switching port by the conduction path formed in the main valve. In the flow path switching valve which switches the communication destination of the port and maintains the seated state of the main valve by the differential pressure between the pressure control space in the valve chamber leading to the high pressure port and the conduction path of the main valve A pressure equalizing hole formed in the main valve for conducting the conduction path and the pressure control space; and disposed close to the main valve and rotatable about an axis of the valve chamber. A sub-valve, a driving means for rotating the sub-valve, and a rotation range of the main valve in the low pressure A main valve stopper mechanism that restricts the rotation range between two positions of a first position and a second position, which are selectively communicated with the switching port, and the sub valve and the main valve are connected / not connected. A clutch mechanism to be connected, and the sub valve opens the pressure equalizing hole in a predetermined angle range with respect to the main valve of the sub valve and closes the pressure equalizing hole at a position other than the predetermined angle range. The clutch mechanism is configured such that the main valve is connected to the sub valve at a substantially central position in the predetermined angle range in which the sub valve opens the pressure equalizing hole, and the main valve stopper mechanism regulates the clutch mechanism. When the sub valve rotates so as to be out of the rotation range of the main valve, the main valve is disconnected from the sub valve, and the pressure equalizing hole is opened by the rotation of the sub valve. And the main valve is rotated together with the auxiliary valve by the clutch mechanism. .

  The flow path switching valve according to claim 2 is the flow path switching valve according to claim 1, wherein a part of the opposite surfaces of the main valve and the subvalve on the same circumference around the axis, A roof-shaped ridge having a ridge line in the circumferential radial direction is formed, and biasing means for biasing the auxiliary valve in the main valve direction so as to be separable from the main valve is provided, The sub-valve and the main valve are connected when the inclined surfaces of the sub-valve and the main valve are in contact with each other, and the two protuberances rest on each other's ridgeline against the biasing force of the biasing means. The clutch mechanism is configured so that the sub-valve and the main valve are disconnected from each other by exceeding.

  The flow path switching valve according to claim 3 is the flow path switching valve according to claim 2, wherein the protrusions of the sub valve and the main valve are respectively provided at two locations spaced 180 degrees around the circumference. It is formed.

  A compressor with a flow path switching valve according to claim 4 is a compressor with a flow path switching valve provided with the flow path switching valve according to claim 1, 2, or 3, wherein the high pressure space and the low pressure of the compressor body are provided. A block-shaped housing that forms a space, and the valve chamber of the flow path switching valve, the high-pressure port, the low-pressure port, and the switching port are formed in the housing itself by drilling in the housing, respectively. The high pressure port and the low pressure port of the housing are opened to the low pressure space and the high pressure space, respectively.

  An air conditioner according to a fifth aspect includes the flow path switching valve according to the first, second, or third aspect.

  An air conditioner according to a sixth aspect is equipped with the compressor with the flow path switching valve according to the fourth aspect.

  2. The flow path switching valve according to claim 1, wherein the main valve is rotated by a rotation range between two positions of a first position and a second position where the low pressure port is selectively communicated with the switching port by the main valve stopper mechanism. Regulated by When the main valve is in the first position and the sub-valve is rotated by the driving means so that the pressure equalization hole of the main valve enters the predetermined angle range, the pressure equalization between the conduction path and the pressure control space is started. When the central position is within a predetermined angle range, the main valve is connected to the sub valve by the clutch mechanism, and the main valve rotates together with the sub valve while the pressure equalizing hole is opened by the rotation of the sub valve. The rotation of the main valve advances, the main valve stops at the second position by the main valve stopper mechanism, the clutch mechanism is disconnected, and only the sub valve rotates. The auxiliary valve closes the pressure equalizing hole at a position outside the predetermined angle range. By rotating the auxiliary valve in the reverse direction, the main valve is similarly switched from the second position to the first position.

  Pressure equalization is started when the pressure equalization hole is within a predetermined angle range by the rotation of the sub valve. That is, the pressure equalization is started before reaching the substantially central position of the predetermined angle range (before the clutch mechanism is engaged) and is sufficiently equalized when the clutch mechanism is engaged. Can be performed reliably. Since the auxiliary valve only needs to be rotated coaxially with the main valve, the structure becomes very simple.

  In the flow path switching valve according to claim 2, when the protrusion of the clutch mechanism is not in contact, the connection state is established, and when the protrusion of the main valve and the auxiliary valve is in contact, the connection state is established. When the connected state is changed to the disconnected state, the main valve is forcibly stopped at the first position or the second position by the main valve stopper mechanism, so that the biasing force of the biasing means is resisted by the rotation of the sub valve. Thus, both ridges ride over each other's ridgeline and become unconnected.

  In the flow path switching valve according to claim 3, in the flow path switching valve according to claim 2, the protrusions of the sub valve and the main valve are respectively formed at two positions spaced 180 degrees around the circumference. When the clutch mechanism is in the connected state, the ridges come into contact with both sides sandwiching the center of rotation, so that the rotation is balanced and the rotation operation is performed reliably.

  5. The compressor with a flow path switching valve according to claim 4, wherein the housing is a block-shaped member that forms a high-pressure space and a low-pressure space. The housing is provided with a valve chamber of a flow path switching valve, a high pressure port, a low pressure port, and a switching port, and the high pressure port and the low pressure port of the housing open to a low pressure space and a high pressure space, respectively. ing. The port and the valve chamber are formed by the housing itself, and there is no pipe for the flow path switching valve outside the compressor with the flow path switching valve.

  In the air conditioner of claim 5, the effect of the flow path switching valve of claim 1, 2, or 3 is achieved.

  In the air conditioner of claim 6, the effect of the compressor with the flow path switching valve of claim 4 is exhibited.

  According to the flow path switching valve of the first aspect, the pressure equalization is started before the clutch mechanism is connected, and the pressure is sufficiently equalized when the clutch mechanism is connected. In addition to being able to perform reliably, the sub-valve only needs to be rotated coaxially with the main valve, so that the structure becomes extremely simple, and the operation can be smoothly performed with a simple configuration, thereby increasing the reliability.

  According to the flow path switching valve of claim 2, in addition to the effect of claim 1, the structure of the clutch mechanism can be simplified.

  According to the flow path switching valve of the third aspect, in addition to the effect of the second aspect, the clutch mechanism is balanced in the rotational state of the sub-valve and the main valve so that the rotational operation is performed reliably. Can be done smoothly.

  According to the compressor with a flow path switching valve of claim 4, in addition to the effect of claim 1, 2, or 3, the port and the valve chamber are formed by the housing itself, Since there is no piping for the flow path switching valve, the outer piping is reduced as much as possible, and a synergistic effect of the flow path switching valve and the on-vehicle compressor is obtained, improving reliability, saving space, saving energy, and saving resources. Can contribute.

  According to the air conditioner of claim 5, the effect of claim 1, 2, or 3 is obtained.

  According to the air conditioner of claim 6, the effect of claim 4 is obtained.

  Next, embodiments of a flow path switching valve, a compressor with a flow path switching valve, and an air conditioner according to the present invention will be described with reference to the drawings.

  FIG. 1 is an exploded perspective view of main parts of a flow path switching valve according to an embodiment of the present invention, FIG. 2 is a partially broken perspective view of a compressor with a flow path switching valve using the flow path switching valve, and FIG. Is a partial vertical cross-sectional view of the compressor with the flow path switching valve, FIG. 4 is a cross-sectional view of a compression portion of the compressor, FIG. 5 is a vertical cross-sectional view of the compressor, and FIG. FIG. 7 is a diagram showing a refrigeration cycle of an air conditioner using the compressor. 3 shows a cross section taken along the line AA of FIG. 6, FIG. 5 shows a cross section taken along the line BB of FIG. 6, and in the compression section 10 of FIG. In the following description, the vertical direction in the figure will be described as the vertical direction of the compressor. Note that the compressor 10 of the compressor body shown in FIG. 4 is the same as the conventional one, and a part thereof is shown in a simplified manner.

  The compressor with a flow path switching valve of this embodiment is an in-vehicle compressor, and the refrigeration cycle in FIG. 7 constitutes an in-vehicle air conditioner. The main body of the compressor is configured by attaching a housing 1 to a compression unit 10, and a C switching port 23 and an E switching port 24 described later are formed in the housing 1. In FIG. 7, the positions of the C switching port 23 and the E switching port 24 are shifted in order to show the cycle path. The C switching port 23 is connected to the outdoor unit 20, the capillary 30, the indoor unit 40, and the E switching port 24 by piping, so that a refrigeration cycle is configured. During the cooling operation, the refrigerant discharged from the compressor main body 100 circulates through the C switching port 23 → the outdoor unit 20 → the capillary 30 → the indoor unit 40 → the E switching port 24, and the outdoor unit 20 is the condenser and the indoor unit 40. Functions as an evaporator and cools the passenger compartment. Further, during the heating operation, the refrigerant is circulated in reverse, the indoor unit 40 functions as a condenser, and the outdoor unit 20 functions as an evaporator, thereby heating the vehicle interior. “C” and “E” of the C switching port 23 and the E switching port 24 are names based on the cooling operation.

  As shown in FIG. 4, the compression unit 10 of the compressor body is configured by sealing a front case 10a with a valve block 10b, and in the front case 10a, a cylinder block 10c, a drive shaft 10d, and a swing plate. 10e is accommodated. A cylinder bore 10f is formed in the cylinder block 10c, and a piston 10g is disposed in the cylinder bore 10f. The piston 10g is connected to a swing plate 10e, and the swing plate 10e is swingably attached to the drive shaft 10d. Further, a discharge passage 10j and a suction passage 10k are formed in the valve block 10b. The discharge passage 10j is opened and closed by a discharge valve 10m, and the suction passage 10k is opened and closed by a suction valve 10n.

  With the above configuration, when the rotational power of the vehicle engine (not shown) is transmitted to the drive shaft 10d via the pulley 10p and the drive shaft 10d rotates, the swing plate 10e swings by a mechanism (not shown), and the piston 10g becomes the cylinder bore 10f. Reciprocates within. Thereby, the suction of the refrigerant gas from the suction passage 10k and the discharge of the refrigerant gas from the discharge passage 10j are repeated. Note that the pressure in the front case 10a is adjusted by a pressure control valve (not shown), and as the pressure increases, the inclination angle of the swing plate 10e decreases, the stroke of the piston 10g decreases, and the discharge capacity decreases. . When the pressure in the front case 10a decreases, the inclination angle of the swing plate 10e increases as the pressure decreases, and the stroke of the piston 10g increases and the discharge capacity increases. Thereby, the driving capability of the compressor body is controlled.

  A housing 1 formed of a metal material by die casting, cutting, or the like is attached to the valve block 10b. The housing 1 includes a substantially columnar block portion 1A that matches the shape of the compression portion 10 and a cylindrical case portion 1B formed at one location on the outer periphery of the block portion 1A. The block portion 1A has an outer wall 1a surrounding the periphery, a partition wall 1b formed in a ring shape concentrically with the outer wall 1a inside the outer wall 1a, and an end portion of the drive shaft 10d at the center inside the partition wall 1b. The bearing portion 1c to be passed is molded integrally. A space between the outer wall 1a and the partition wall 1b is a high-pressure space sp1, a space inside the partition wall 1b is a low-pressure space sp2, a discharge passage 10j is opened in the high-pressure space sp1, and a suction passage 10k is formed in the low-pressure space sp2. It is open.

  A case portion 1B of the housing 1 is cut into a cylindrical shape to form a case main body of the flow path switching valve according to the embodiment, and a valve chamber 11 is formed therein. The bottom surface of the valve chamber 11 is a valve seat 12, and the upper end of the case portion 1 </ b> B is fitted with a lid 13 that holds a drive unit 5 described later. The lid body 13 has a cylinder portion 13a fitted in the valve chamber 11, and the valve chamber 11 is sealed by a ring 13a1 on the outer periphery of the cylinder portion 13a. The valve seat 12 has a D port 21 that communicates the valve chamber 11 and the high pressure space sp1, an S port 22 that communicates the valve chamber 11 and the low pressure space sp2, and a C switch that communicates the valve chamber 11 and the outside of the housing 1. A port 23 and an E switching port 24 are formed. A main valve stopper pipe 21 a is inserted into the D port 21, and the main valve stopper pipe 21 a protrudes into the valve chamber 11 from the valve seat 12. Further, the S port 22, the C switching port 23, and the E switching port 24 are cut vertically from the valve seat 12, and are bent at a right angle by cutting from the low pressure space sp2 side and the end face of the housing 1, respectively. ing.

  A main valve 3 is disposed in the valve chamber 11. The main valve 3 is made of resin and is rotatably supported by a shaft 12a standing at the center of the valve seat 12. The main valve 3 has a bearing portion through which the shaft 12a penetrates, and has a horizontal cross-section arc-shaped stopper portion 3A sliding along the main valve stopper tube 21a on one side of the bearing portion, and a low pressure on the opposite side. It has a conducting part 3B. In the low-pressure conducting part 3B, a vertically long dome-like conducting path 31 opened on the valve seat 12 side is formed, and this conducting path 31 is an alternative to the S switching port 23 or the E switching port 24. Can be conducted. A seal portion 31 a that slightly protrudes toward the valve seat 12 is formed around the opening of the conduction path 31, and this seal portion 31 a contacts the sliding surface of the valve seat 12.

  A piston ring 32 is disposed on the outer periphery of the upper portion of the main valve 3, and this piston ring 32 is in sliding contact with the inner surface of the cylinder portion 13 a of the lid body 13. The space above the main valve 3 in the cylinder portion 13a is a pressure control space R. A slight gap is formed between the cylinder portion 13a and the piston ring 32.

  As shown in FIG. 1, a circular flat plate-shaped sub valve seat 33 is formed around the shaft 12a on the upper end surface of the main valve 3 on the pressure control space R side. A pressure equalizing hole 34 communicating with the conduction path 31 in the low-pressure conduction part 3B is formed. Further, on the outer periphery of the auxiliary valve seat 33, protrusions 35, 35 are formed at two positions spaced apart by 180 °. Further, on the upper surface of the main valve 3, a sub valve stopper 36 having an arcuate horizontal section is formed on a part of the outer periphery of the sub valve seat 33.

  A disc-shaped auxiliary valve 4 is disposed on the auxiliary valve seat 33. The sub-valve 4 has a driven shaft 41 to which a shaft 53 of the driving unit 5 described later is fitted at the center, and a predetermined radial position on the outer periphery of the driven shaft 41 corresponding to the pressure equalizing hole 34 of the sub-valve seat 33. A pressure equalizing groove 42 penetrating the auxiliary valve 4 is formed in an arc shape at an angle. Further, as shown in FIG. 8, on the surface of the auxiliary valve 4 on the main valve 3 side, similarly to the protrusions 35, 35 of the main valve 3, the radial position corresponding to the protrusions 35, 35 is 180 °. Separated protrusions 43 and 43 are formed. The inner surfaces of the protrusions 43, 43 (around the pressure equalizing groove 42) are in close contact with the sub valve seat 33 on the main valve 3 side. Further, a fan-shaped stopper piece 44 capable of contacting the auxiliary valve stopper 36 is formed on a part of the outer periphery of the auxiliary valve 4.

  The drive unit 5 includes a cylindrical case 51 fixed to the upper end of the lid body 13. In the case 51, a magnet rotor 52 is disposed. The rotor 52 is attached to a shaft 53, and the shaft 53 is rotatably fitted in a bearing 13b extending at the upper end of the lid 13. Are combined. The sub valve 4 is urged downward by a spring 54 disposed around the driven shaft 41 and the lower end of the shaft 53. As shown in FIG. 1, the lower end portion of the shaft 53 is a bifurcated engagement portion 53 a, and this engagement portion 53 a is engaged with the driven shaft 41 of the sub valve 4. A drive coil 55 is disposed on the outer periphery of the case 51, and the drive coil 55, the rotor 52, and the shaft 53 constitute a stepping motor as drive means.

  Both the ridge 35 of the main valve 3 and the ridge 43 of the sub-valve 4 have a roof shape having a ridge line in the circumferential radial direction, and the ridges 35 and 43 constitute a clutch mechanism. When the inclined surfaces of the protrusions 43 and 35 are in contact with each other, the auxiliary valve 4 is urged toward the main valve 3 by the spring 54 of the drive unit 5. Is held, and the main valve 3 rotates together with the sub-valve 4. That is, the clutch mechanism is in a connected state. On the other hand, when the end of the stopper portion 3A of the main valve 3 comes into contact with the main valve stopper tube 21a, the main valve 3 is prevented from rotating, and when the sub valve 4 is further rotated, it resists the biasing force of the spring 54. Then, the ridge line of the ridge 43 of the sub-valve 4 rides over the ridge line of the ridge 35 of the main valve 3, and the contact state of the ridges 43, 35 is released. That is, the clutch mechanism is disconnected. Thus, by driving the drive unit 5, the sub-valve 4 rotates independently with respect to the main valve 3 when the protrusions 43, 43 do not contact the main valve 3 protrusions 35, 35. , 43 are brought into contact with the ridges 35, 35 and are rotated with the main valve 3.

  Next, the operation of the flow path switching valve of the embodiment will be described. FIG. 9 is an operation explanatory diagram of the flow path switching valve of the embodiment. FIG. 9 shows the positional relationship of each part, and the notation such as a solid line, a broken line, and a slanted line does not indicate the front-rear position or structure. The notation “D, S, C, E” indicates the opening in the valve seat 12 of the D port 21, the S port 22, the C switching port 23, and the E switching port 24. 9A shows the cooling operation state, FIG. 9D shows the heating operation state, and FIGS. 9B and 9C show the switching process of the operation state. In the valve seat 12, the D port 21 and the S port 22 are opened at positions separated by 180 °, and the C switching port 23 and the E switching port 24 are opened at an angle slightly smaller than 90 ° from the S port 22. Has been.

  First, it is assumed that the cooling operation shown in FIG. As shown in FIG. 9A, the D port 21 is electrically connected to the C switching port 23, and the S port 22 is electrically connected to the E switching port 24 by the conduction path 31. And the high pressure refrigerant | coolant is introduce | transduced from the D port 21, the valve chamber 11 becomes high pressure, and the conduction path 31 is low pressure. At this time, the pressure equalizing hole 34 is closed by the auxiliary valve 4 as shown in FIG. Therefore, the pressure control space R above the main valve 3 becomes high pressure, and the main valve 3 is seated on and closely contacted with the valve seat 12 by the pressure difference between the pressure control space R and the conduction path 31.

  Next, when switching from the cooling operation state to the heating operation state, the compressor main body remains in the operation state, and the stepping motor is driven to rotate the auxiliary valve 4 counterclockwise from the state of FIG. . 9B, the pressure equalizing hole 34 is opened by the pressure equalizing groove 42 of the sub-valve 4 so that the conduction path 31 and the pressure control space R are equalized, and the pressure control space R becomes low pressure. Become. In the state of FIG. 9B, the pressure equalizing hole 34 is at the center position of the pressure equalizing groove 42. However, since the pressure equalizing groove 42 has a predetermined angle in an arc shape, The pressure equalization is started from the position where the pressure equalization hole 34 spans the pressure equalization groove 42, and the pressure is sufficiently equalized in the state of FIG. 9B. Therefore, the main valve 3 is separated (floated) from the valve seat 12 by the high pressure of the refrigerant discharged from the D port 21.

  9B, the protrusions 43, 43 of the auxiliary valve 4 come into contact with the protrusions 35, 35 of the main valve 3. Therefore, when the auxiliary valve 4 further rotates counterclockwise, The valve 3 rotates together with the auxiliary valve 4 to be in the state shown in FIG. As a result, the end of the stopper portion 3A abuts against the main valve stopper tube 21a to prevent the main valve 3 from rotating, the D port 21 is conducted to the E switching port 24, and the S port 22 is conducted to the conduction path 31. Is conducted to the C switching port 23. When the sub-valve 4 further rotates, the clutch mechanism by the protrusions 43 and 35 is disengaged, and only the sub-valve 4 rotates, and the state shown in FIG. At this time, the pressure equalizing hole 34 is closed by the auxiliary valve 4, and the stopper piece 44 of the auxiliary valve 4 comes into contact with the auxiliary valve stopper 36 to stop the rotation of the auxiliary valve 4. As a result, the pressure control space R becomes high pressure, and the main valve 3 is seated on and closely contacts the valve seat 12 due to the differential pressure between the pressure control space R and the conduction path 31.

  When switching from the heating operation state to the cooling operation state, if the auxiliary valve 4 is rotated counterclockwise from the state of FIG. 9D, the pressure control space R and the conduction path 31 in the state of FIG. 9C. And the clutch mechanism is in a connected state, the sub valve 4 further rotates, and the main valve rotates together. 9B, the end of the stopper portion 3A abuts the main valve stopper tube 21a to prevent the main valve 3 from rotating, and the clutch mechanism is disengaged and the sub valve 4 is further disengaged. It turns to the state of FIG. 9 (A).

  In the case of this reverse rotation, the positional relationship between the pressure equalizing groove 42 and the pressure equalizing hole 34 is as shown in FIG. Although slightly deviated from (C), the pressure equalizing groove 42 has a predetermined angle, so that the pressure is sufficiently equalized when the clutch mechanism shifts to the non-connected state.

  The housing 1 has a block shape, and the valve chamber 11, the D port 21, the S port 22, the C switching port 23, and the E switching port 24 are formed in the housing 1 by being formed in the housing 1. Therefore, there is no pipe for the flow path switching valve outside the compressor body, and the outside pipe is reduced as much as possible.

  In the above embodiment, the swash plate type has been described as an example of the compressor body, but a scroll type compressor body may be used.

It is a principal part disassembled perspective view of the flow-path switching valve concerning embodiment of this invention. It is a partially broken principal part perspective view of the compressor with a flow-path switching valve using the same flow-path switching valve. It is AA partial longitudinal cross-sectional view of the compressor with a flow-path switching valve. Sectional view of the compression part of the compressor, It is a BB longitudinal cross-sectional view of the compressor. It is a top view of the housing part of the compressor. It is a figure which shows the refrigerating cycle of the air conditioner using the compressor. It is a back surface perspective view of a subvalve in an embodiment. It is operation | movement explanatory drawing of the flow-path switching valve of embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Housing 11 Valve chamber 12 Valve seat R Pressure control space sp1 High pressure space sp2 Low pressure space 21 D port 21a Main valve stopper pipe 22 S port 23 C switching port 24 E switching port 3 Main valve 3A Stopper part 31 Conduction path 33 Sub valve seat 34 Pressure equalizing hole 35 Projection 4 Sub valve 42 Pressure equalizing groove 43 Projection 5 Drive unit 52 Rotor 53 Shaft 54 Spring 55 Drive coil 10 Compression unit 20 Outdoor unit 30 Capillary 40 Indoor unit

Claims (6)

A main valve is accommodated in a cylindrical valve chamber so as to be rotatable about an axis of the valve chamber, and a low pressure port and two switching ports are opened in a valve seat facing the main valve, and formed in the main valve. The low pressure port communicates with one switching port through the conducting path, and the main valve is rotated to switch the communication destination of the two switching ports so that the high pressure port communicates with the other switching port. In the flow path switching valve configured to maintain the seating state of the main valve by the differential pressure between the pressure control space in the valve chamber leading to the inside of the conduction path of the main valve,
A pressure equalizing hole formed in the main valve and conducting the conduction path and the pressure control space;
A sub-valve arranged close to the main valve so as to be rotatable about an axis of the valve chamber and opening and closing the pressure equalizing hole;
Driving means for rotating the auxiliary valve;
A main valve stopper mechanism for restricting a rotation range of the main valve to a rotation range between two positions of a first position and a second position where the low-pressure port is selectively communicated with the switching port;
A clutch mechanism for connecting / disconnecting the sub valve and the main valve;
The sub valve is formed in a shape that opens the pressure equalizing hole in a predetermined angle range with respect to the main valve of the sub valve and closes the pressure equalizing hole at a position other than the predetermined angle range,
In the clutch mechanism, the main valve is connected to the sub valve at a substantially central position in the predetermined angle range where the sub valve opens the pressure equalizing hole, and the main valve rotation range regulated by the main valve stopper mechanism. The main valve is a mechanism that is disconnected from the sub-valve when the sub-valve rotates so as to be disengaged from the
A flow path switching valve characterized in that the main valve is rotated together with the auxiliary valve by the clutch mechanism in a state where the pressure equalizing hole is opened by the rotation of the auxiliary valve. A roof-shaped ridge having a ridge line in the radial direction of the circumference is formed on a part of the opposite circumference of the main valve and the sub-valve on the same circumference around the axis. Urging means for urging in the main valve direction so as to be separable from the main valve;
The sub-valve and the main valve are connected to each other when the inclined surfaces of the sub-valve and the main valve are in contact with each other, and the two ridges cross each other's ridgeline against the urging force of the urging means. So that the sub-valve and the main valve are disconnected from each other.
The flow path switching valve according to claim 1, wherein the clutch mechanism is configured.   3. The flow path switching valve according to claim 2, wherein the protrusions of the sub valve and the main valve are formed at two locations 180 degrees apart from each other around the circumference. A compressor with a flow path switching valve comprising the flow path switching valve according to claim 1,
A block-shaped housing that forms a high-pressure space and a low-pressure space of the compressor body is provided, and the valve chamber of the flow path switching valve, the high-pressure port, the low-pressure port, and the switching port are formed in the housing, respectively. The compressor with a flow path switching valve is formed by the housing itself, and the high pressure port and the low pressure port of the housing are opened to the low pressure space and the high pressure space, respectively.   An air conditioner equipped with the flow path switching valve according to claim 1, 2 or 3.   An air conditioner equipped with the compressor with a flow path switching valve according to claim 4.

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