JP2004332709A - Piston type compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To efficiently inhibit generation of abnormal noise by adjusting suction initiation timing according to the operating condition of a piston type compressor, in the piston type compressor using a rotary valve as an intake valve. <P>SOLUTION: A suction valve arrangement 55 is provided with a rotary valve 35 with a suction guide hole 37 which introduces refrigerant gas from a suction chamber 27 to a compression chamber 26. A valve hole 43a which is always connected to the suction chamber 27, and a connecting hole 47 which is connected to the compression chamber 26 in a stroke of increasing capacity ahead of the suction guide hole 37 are formed in the rotary valve 35. The poppet 44 opens or closes between the valve hole 43a and the connecting hole 47 corresponding to a difference between a force based on pressure on the suction chamber 27 which acts in the valve opening direction and a force based on pressure on the compressed chamber 26 which acts in the valve closing direction, thus the actual inhalation initiation timing is prevented from being delayed from an optimal inhalation initiation timing. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a piston type compressor using a rotary valve as a suction valve.
[0002]
[Prior art]
For example, in a piston type compressor used as a refrigerant compressor of a vehicle air conditioner, a suction valve including a reed valve is generally used. When the pressure on the compression chamber side becomes smaller than the pressure on the suction pressure area side during the volume increase stroke of the compression chamber in which the piston moves from the top dead center position to the bottom dead center position side, the refrigerant gas in the suction pressure area becomes the suction valve. Is pushed out and flows into the compression chamber. Such a suction valve composed of a differential pressure valve such as a reed valve always guarantees an optimal suction start timing (hereinafter referred to as a suction start timing) in suctioning the refrigerant gas from the suction pressure region to the compression chamber. However, an intake valve formed of a differential pressure valve is likely to generate abnormal noise due to self-excited vibration.
[0003]
Therefore, there has been a piston type compressor using a rotary valve that does not generate self-excited vibration as a suction valve. The rotary valve is provided with a suction guide passage which is always in communication with the suction pressure region, and the compression chamber side of the suction guide passage is opened at the outer peripheral surface of the rotary valve. The rotary valve rotates in synchronization with the rotating shaft, thereby sequentially connecting the suction guide passage to the compression chamber in the volume increasing process.
[0004]
Now, in a piston type compressor using a rotary valve as a suction valve, the timing of starting the suction of the refrigerant gas from the suction pressure region to the compression chamber is determined by the opening position of the suction guide passage on the outer peripheral surface of the rotary valve. However, the optimal suction start timing differs depending on the operating conditions of the piston type compressor. In other words, the optimum suction start timing differs depending on a change in suction pressure due to a change in the rotational speed of the piston type compressor, and a change in suction pressure due to a change in the discharge capacity in a variable displacement type piston compressor. Therefore, when a rotary valve is used as a suction valve, it is difficult to always match the actual suction start timing with the optimum suction start timing.
[0005]
Therefore, for example, when the actual suction start timing is earlier than the optimum suction start timing, the pressure of the refrigerant gas remaining in the compression chamber is higher than the pressure of the suction guide passage communicating with the suction pressure region. Therefore, the refrigerant in the compression chamber flows backward to the suction guide passage side of the rotary valve, and large suction pulsation occurs. The suction pulsation causes abnormal noise. Further, when the high-temperature refrigerant gas in the compression chamber flows backward to the suction guide passage side, the refrigerant gas sucked into the other compression chambers is heated and expanded, and the volume efficiency of the piston compressor is reduced.
[0006]
Conversely, if the actual suction start timing is too late from the optimal suction start timing, the pressure in the compression chamber will be too lower than the pressure in the suction pressure region. Due to this pressure difference, the refrigerant gas rapidly flows into the compression chamber, and a large suction pulsation is generated.
[0007]
In order to solve such a problem, it has been proposed to form a notched passage at the opening edge of the suction guide passage on the outer peripheral surface of the rotary valve (for example, see Patent Document 1). The notch passage is formed on the leading side in the rotation direction of the rotary valve with respect to the opening of the suction guide passage. Therefore, since the notch passage communicates with the compression chamber prior to the other part of the opening of the suction guide passage, the inflow and outflow of the refrigerant gas into and from the compression chamber at the start of the communication between the opening and the compression chamber are reduced. Only a small amount is allowed.
[0008]
Therefore, for example, even when the actual suction start timing is earlier than the optimum suction start timing, the reverse flow rate of the refrigerant gas from the compression chamber to the suction guide passage side is small, and the generation of suction pulsation and the reduction in volumetric efficiency are reduced. Can be suppressed. Conversely, even when the actual suction start timing is too late than the optimal suction start timing, it is possible to suppress the rapid inflow of the refrigerant gas from the suction guide passage into the compression chamber and suppress the occurrence of suction pulsation. be able to.
[0009]
[Patent Document 1]
JP-A-5-164444
[0010]
[Problems to be solved by the invention]
However, in the technique of Patent Literature 1, although the amount is small, the notch passage still allows the refrigerant gas to flow into and out of the compression chamber. In other words, when the technique of Patent Document 1 is adopted, it is not possible to prevent the actual suction start timing from deviating from the optimal suction start timing. Therefore, it is possible to effectively prevent the occurrence of the problem such as abnormal noise caused by the deviation. It is hard to say that it can be suppressed.
[0011]
SUMMARY OF THE INVENTION It is an object of the present invention to effectively suppress the generation of abnormal noise in a piston type compressor using a rotary valve as a suction valve by adjusting the suction start timing according to the operating conditions of the piston type compressor. Is to do.
[0012]
[Means for Solving the Problems]
In order to achieve the above object, according to the first aspect of the present invention, a suction timing adjusting passage is formed in a rotary valve. A first end of the suction timing adjustment passage is always in communication with the suction pressure region, and a second end of the suction timing adjustment passage is in communication with the compression chamber in the volume increasing process prior to the suction guide passage. You. In the rotary valve, a suction timing control valve is provided on the suction timing control passage. The valve body provided in the suction timing control valve is configured to control the suction timing according to a difference between a force based on the pressure on the suction pressure region side acting in the valve opening direction and a force based on the pressure on the compression chamber side acting in the valve closing direction. Open or close the control passage.
[0013]
Therefore, when the pressure on the compression chamber side is higher than the pressure on the suction pressure area side in a state in which the second end of the suction timing adjustment passage communicates with the compression chamber in the volume increasing stroke earlier than the suction guide passage. In this case, the suction timing control valve maintains the closed state of the suction timing control passage by a force based on the pressure on the compression chamber side. Therefore, the timing of starting the suction of gas from the suction pressure region to the compression chamber is delayed, and the pressure in the compression chamber decreases due to an increase in the volume of the compression chamber during that time. As a result, the backflow of gas from the compression chamber to the suction pressure area at the start of communication between the compression chamber and the suction pressure area can be suppressed, and the generation of suction pulsation and a decrease in volumetric efficiency due to this backflow can be suppressed. can do.
[0014]
When the pressure at the compression chamber side becomes lower than the pressure at the suction pressure area side in a state where the second end of the suction timing adjustment passage communicates with the compression chamber in the volume increasing stroke earlier than the suction guide passage. The suction timing control valve immediately opens the suction timing control passage by a force based on the pressure in the suction pressure region. Therefore, it is possible to suppress the timing of starting the suction of the gas from the suction pressure region into the compression chamber from being greatly delayed from the optimal timing, and it is possible to suppress the rapid flow of the gas from the suction pressure region into the compression chamber. Therefore, it is possible to suppress the generation of the suction pulsation caused by the rapid gas inflow.
[0015]
As described above, according to the present invention, the suction start timing can be adjusted in accordance with the operating conditions of the piston type compressor. And the like can be effectively suppressed.
[0016]
It is sufficient for the suction timing control passage and the suction timing control valve to be able to adjust the start timing of gas suction from the suction pressure region to the compression chamber, and to introduce main gas from the suction pressure region to the compression chamber through the suction guide passage. Done through. Therefore, in the suction timing control valve, the maximum distance of the valve body from the seating position may be small, and the problem of self-excited vibration of the valve body due to the use of the differential pressure valve (suction timing control valve) can be avoided.
[0017]
According to a second aspect of the present invention, in the first aspect, the time when the communication between the second end of the suction timing adjustment passage and the compression chamber is started is during the volume reduction stroke of the compression chamber or at the end of the volume reduction stroke ( (When the piston is located at the top dead center).
[0018]
Therefore, for example, even when the optimal suction start timing of the gas from the suction pressure region to the compression chamber comes immediately after the compression chamber shifts from the volume reduction stroke to the volume increase stroke, the suction timing adjustment valve controls the suction timing adjustment passage. Can be opened immediately. Therefore, it is possible to more effectively suppress the rapid flow of gas from the suction pressure region to the compression chamber.
[0019]
According to a third aspect of the present invention, in the first or second aspect, the suction timing adjusting valve is a poppet valve. The poppet valve is less likely to generate self-excited vibration than a reed valve, for example.
[0020]
According to a fourth aspect of the present invention, in the third aspect, the poppet as a valve element included in the suction timing adjustment valve is configured to be capable of opening and closing the suction timing adjustment passage by sliding along a rotation center axis of the rotary valve. Have been. Therefore, it is easy to realize a configuration in which the rotary valve is provided with the suction timing adjusting valve composed of the poppet valve. That is, in general, the radial direction inside the rotary valve is tighter in space in the radial direction than in the direction of the rotation center axis, while the poppet valve requires a large arrangement space in the moving direction of the poppet.
[0021]
According to a fifth aspect of the present invention, in the fourth aspect, the poppet is arranged such that a center axis of the poppet coincides with a rotation center axis of the rotary valve. Therefore, the rotation balance of the rotary valve can be improved. Therefore, for example, as compared with the case where the rotation center axis of the rotary valve is displaced from the center axis of the poppet, the unbalanced load acting on the rotary valve can be reduced, and the durability of the rotary valve can be improved. . Further, in the rotary valve, a structure (for example, a cylindrical wall) for holding the poppet can be provided coaxially with the rotation center axis. For example, as compared with a case where the structure is provided at a position shifted from the rotation center axis. Thus, the processing cost of the rotary valve can be reduced.
[0022]
According to a sixth aspect of the present invention, in the fifth aspect, the poppet is arranged so as to be slidable with respect to the cylindrical inner surface of the outer peripheral wall provided in the rotary valve in the rotary valve. That is, the outer peripheral wall of the rotary valve also serves as a cylindrical wall that slidably holds the poppet. Therefore, in the rotary valve, there is no need to provide a cylindrical wall for slidably holding the poppet separately from the outer peripheral wall, and the processing cost of the rotary valve can be further reduced.
[0023]
According to a seventh aspect of the present invention, in the first or second aspect, the suction timing adjusting valve is a reed valve. The reed valve has a simpler configuration than, for example, a poppet valve, which leads to a reduction in man-hours for manufacturing the suction timing control valve.
[0024]
According to an eighth aspect of the present invention, in addition to any one of the first to seventh aspects, in addition to the first valve portion that opens and closes the suction timing adjustment passage, the suction guide includes the valve body included in the suction timing adjustment valve. A second valve portion for adjusting the degree of opening of the passage is provided.
[0025]
The second valve portion increases the opening of the suction guide passage when the first valve portion opens the suction timing adjustment passage. In other words, for example, the second valve unit may open the suction timing adjustment passage at the time when the communication between the suction guide passage and the compression chamber is started (when the suitable suction start timing is reached). Or in a situation where it has already passed), the opening degree of the suction guide passage is increased. Therefore, the gas is smoothly sucked from the suction pressure region to the compression chamber through the suction guide passage, and the suction efficiency can be improved.
[0026]
The second valve portion reduces the opening of the suction guide passage when the first valve portion closes the suction timing adjustment passage. In other words, for example, the second valve unit may close the suction timing adjustment passage when the communication between the suction guide passage and the compression chamber is started (when a suitable suction start timing is reached). In the case where the operation is not performed), the opening degree of the suction guide passage is reduced. Therefore, the reverse flow rate of the gas from the compression chamber to the suction guide passage can be reduced, and the generation of suction pulsation and a decrease in volumetric efficiency can be more effectively suppressed.
[0027]
That is, in the present invention, by providing the second valve portion in the valve body of the suction timing adjustment valve, it is also suitable for “a large delay of a suitable suction start timing” that cannot be dealt with only by the first valve portion. Can be dealt with.
[0028]
According to a ninth aspect of the present invention, a rotor that rotates in synchronization with the rotation of a rotating shaft opens and closes a gas passage between a suction pressure region and a compression chamber in synchronization with the rotation of the rotating shaft. The piston type compressor provided with the first suction valve has the following characteristic configuration. In addition, it can be said that the rotor provided with the first suction valve forms a so-called rotary valve.
[0029]
The rotor is provided with a second suction valve. The second suction valve has a second port that communicates with the compression chamber in the volume increasing stroke earlier than the first port of the first suction valve. The second suction valve communicates with the second port in accordance with a difference between a force based on the pressure on the suction pressure region side acting in the valve opening direction and a force based on the pressure on the compression chamber side acting in the valve closing direction. It is a configuration that opens or closes the space between the pressure region.
[0030]
Therefore, in a state where the second port of the second suction valve communicates with the compression chamber in the volume increasing stroke earlier than the first port of the first suction valve, the pressure on the compression chamber side is increased. When the pressure is higher than the pressure on the suction pressure region side, the second suction valve maintains a closed state between the second port and the suction pressure region by a force based on the pressure on the compression chamber side. Therefore, the timing of starting the suction of gas from the suction pressure region to the compression chamber is delayed, and the pressure in the compression chamber decreases due to an increase in the volume of the compression chamber during that time. As a result, the backflow of gas from the compression chamber to the suction pressure area at the start of communication between the compression chamber and the suction pressure area can be suppressed, and the generation of suction pulsation and a decrease in volumetric efficiency due to this backflow can be suppressed. can do.
[0031]
Further, in a state where the second port of the second suction valve communicates with the compression chamber in the volume increasing stroke earlier than the first port of the first suction valve, the pressure on the compression chamber side is increased. When the pressure becomes lower than the pressure on the suction pressure region side, the second suction valve immediately opens between the second port and the suction pressure region by a force based on the pressure on the suction pressure region side. Accordingly, it is possible to prevent the start timing of the gas suction from the suction pressure region into the compression chamber from being greatly delayed from the optimal timing, and to prevent the gas from flowing from the suction pressure region to the compression chamber at the start of the communication between the compression chamber and the suction pressure region. A rapid inflow can be suppressed. Therefore, it is possible to suppress the generation of the suction pulsation caused by the rapid gas inflow.
[0032]
As described above, according to the present invention, the suction start timing can be adjusted in accordance with the operating conditions of the piston type compressor. And the like can be effectively suppressed.
[0033]
It is sufficient for the second suction valve (second port) to be able to adjust the start timing of gas suction from the suction pressure region to the compression chamber, and the main gas is introduced from the suction pressure region to the compression chamber in the first state. This is performed via a suction valve (first port). Accordingly, the opening amount of the second port by the second suction valve may be small, and the problem of self-excited vibration of the valve element due to the use of the differential pressure valve (second suction valve) can be avoided.
[0034]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, first to fourth embodiments in which the piston type compressor of the present invention is embodied as a variable capacity swash plate type compressor (hereinafter referred to as a compressor) for compressing a refrigerant used in a vehicle air conditioner will be described. In the second to fourth embodiments, only differences from the first embodiment will be described, and the same or corresponding members will be denoted by the same reference numerals and description thereof will be omitted.
[0035]
○ 1st embodiment
First, the compressor will be described.
As shown in FIG. 1, a compressor 10 includes a cylinder block 11, a front housing 12 joined and fixed to a front end thereof, and a rear housing joined and fixed to a rear end of the cylinder block 11 via a valve / port forming body 13. 14 is provided. The cylinder block 11, the front housing 12, and the rear housing 14 constitute a housing of the compressor 10. In addition, let the left side of FIG. 1 be the front of the compressor 10, and let the right side be the back.
[0036]
A crank chamber 15 is defined in a region surrounded by the cylinder block 11 and the front housing 12. The rotating shaft 16 is provided so as to penetrate the crank chamber 15, and is rotatably supported between the front housing 12 and the cylinder block 11. The rotating shaft 16 is operatively connected to an engine (not shown) which is a driving source of the vehicle, and is rotated by receiving power from the engine.
[0037]
A lug plate 20 is fixed to the rotation shaft 16 in the crank chamber 15 so as to be integrally rotatable. A swash plate 21 as a cam plate is accommodated in the crank chamber 15. The swash plate 21 is supported by the rotating shaft 16 so as to be slidable and tiltable. The hinge mechanism 22 is interposed between the lug plate 20 and the swash plate 21. Accordingly, the swash plate 21 can be rotated synchronously with the lug plate 20 and the rotating shaft 16 by the hinge connection with the lug plate 20 via the hinge mechanism 22 and supported by the rotating shaft 16. Can be tilted with respect to the rotation shaft 16 while sliding in the direction L of the rotation center axis (hereinafter simply referred to as the axis).
[0038]
The compressor 10 includes a multi-cylinder piston-type compression mechanism. That is, as shown in FIGS. 1 and 2, a plurality (five in this embodiment; only one is shown in FIG. 1) of the cylinder bores 23 is provided at the rear end side of the rotary shaft 16 in the cylinder block 11. The through holes are formed so as to surround each other at a constant angular interval. The single-headed piston 24 is reciprocally accommodated in each cylinder bore 23.
[0039]
As shown in FIG. 1, the front and rear openings of the cylinder bore 23 are closed by a valve / port forming body 13 and a piston 24, and a compression chamber 26 whose volume changes in accordance with the reciprocating motion of the piston 24 in the cylinder bore 23. Is partitioned. Each piston 24 is moored to the outer periphery of the swash plate 21 via a shoe 25. Therefore, the rotation of the swash plate 21 accompanying the rotation of the rotating shaft 16 is converted into the reciprocating motion of the piston 24 via the shoe 25.
[0040]
In the rear housing 14, a suction chamber 27 and a discharge chamber 28, which form a suction pressure area, are respectively defined. The suction chamber 27 is formed at the center of the rear housing 14. The discharge chamber 28 is formed so as to surround the outer periphery of the suction chamber 27. An external pipe connected to a low-pressure side heat exchanger of an external refrigerant circuit (not shown) is connected to the suction chamber 27. An external pipe connected to the high-pressure side heat exchanger of an external refrigerant circuit (not shown) is connected to the discharge chamber 28. The external refrigerant circuit and the compressor 10 constitute a refrigerant circulation circuit (refrigeration cycle).
[0041]
The refrigerant gas in the suction chamber 27 is moved from the top dead center position to the bottom dead center side of each piston 24 to increase the volume of the compression chamber 26, thereby causing the suction valve disposed in the cylinder block 11 to move. It is sucked into the compression chamber 26 via the device 55. The refrigerant gas sucked into the compression chamber 26 is compressed to a predetermined pressure by reducing the volume of the compression chamber 26 by moving from the bottom dead center position of the piston 24 to the top dead center side. The liquid is discharged into the discharge chamber 28 through the discharge port 29 and the discharge valve 30 formed in the formed body 13.
[0042]
A bleed passage 31, an air supply passage 32, and a capacity control valve 33 are provided in the housing of the compressor 10. The bleed passage 31 connects the crank chamber 15 and the suction chamber 27. The bleed passage 31 includes an in-shaft passage 34 formed at the axial position of the rotary shaft 16. The inlet 34a of the in-shaft passage 34 is opened to the crank chamber 15 near the lug plate 20, and the outlet 34b is opened to the rear end face of the rotating shaft 16. The air supply passage 32 connects the discharge chamber 28 and the crank chamber 15. In the middle of the air supply passage 32, a well-known capacity control valve 33 composed of an electromagnetic valve is provided.
[0043]
By adjusting the opening of the capacity control valve 33, the amount of high-pressure discharge gas introduced into the crank chamber 15 through the air supply passage 32 and the amount of gas discharged from the crank chamber 15 through the bleed passage 31 are determined. The balance is controlled, and the pressure in the crank chamber 15 is determined. In accordance with the change in the pressure in the crank chamber 15, the difference between the pressure in the crank chamber 15 via the piston 24 and the pressure in the compression chamber 26 is changed, and the inclination angle of the swash plate 21 is changed. That is, the displacement of the compressor 10 is adjusted.
[0044]
For example, when the pressure in the crank chamber 15 decreases, the inclination angle of the swash plate 21 increases, the stroke of the piston 24 increases, and the displacement of the compressor 10 increases. Conversely, when the pressure in the crank chamber 15 increases, the inclination angle of the swash plate 21 decreases, the stroke of the piston 24 decreases, and the discharge capacity of the compressor 10 decreases.
[0045]
Next, the suction valve device 55 will be described.
As shown in FIGS. 1 and 2, a housing hole 17 having a columnar shape is formed in the center of the cylinder block 11 surrounded by the cylinder bore 23 in the housing of the compressor 10. A boss portion 11a projecting from the rear end surface of the cylinder block 11 around the opening of the housing hole 17 and penetrating through the valve / port forming body 13 and entering the center portion of the rear housing 14 is provided. Therefore, the accommodation hole 17 and the suction chamber 27 are arranged continuously in the direction of the axis L. The accommodation hole 17 and each of the compression chambers 26 are connected to each other via a plurality of (five in the present embodiment) conductive paths 18 formed radially around the axis L in the cylinder block 11.
[0046]
In the accommodation hole 17, a rotary valve 35 as a rotor having a substantially bottomed cylindrical shape having a bottom on the front side is rotatably accommodated. The inner peripheral surface 17a of the housing hole 17 and the outer peripheral surface 35b of the rotary valve 35 are slidably contacted. Inside the front end side of the rotary valve 35, a communication hole 35c is formed penetrating in the front-rear direction. The introduction chamber 36, which is a space in the cylinder of the rotary valve 35, communicates with the shaft passage 34 (outlet 34b) of the rotary shaft 16 through a communication hole 35c. The introduction chamber 36 communicates with the suction chamber 27. The communication hole 35c and the introduction chamber 36 constitute a part of the bleed passage 31.
[0047]
The front end side of the rotary valve 35 has a small diameter (small diameter portion 35a). A mounting hole 16 a is provided on the rear end face of the rotating shaft 16 facing the housing hole 17. A rotary valve 35 is press-fitted and fixed to the mounting hole 16a of the rotating shaft 16 with a small-diameter portion 35a. Therefore, the rotary shaft 16 and the rotary valve 35 are arranged and integrated on the same axis L, and the rotary valve 35 is synchronized with the rotation of the rotary shaft 16, that is, the reciprocating motion of the piston 24, and It is rotated about the axis L. The outer peripheral surface 35b of the rotary valve 35 and the inner peripheral surface 17a of the housing hole 17 constitute a sliding bearing surface that rotatably supports the rear end of the rotating shaft 16.
[0048]
In the outer peripheral wall 39 of the rotary valve 35, a suction guide hole 37 that is always in communication with the introduction chamber 36 is formed in a fixed section in the circumferential direction. The suction guide hole 37 forms a suction guide passage that sequentially connects the introduction chamber 36, that is, the suction chamber 27, and the conduction path 18 extending from each compression chamber 26 in synchronization with the rotation of the rotary valve 35.
[0049]
That is, in the rotary valve 35, the suction guide hole 37 communicates with the conduction path 18 of the cylinder block 11 when the compression chamber 26 shifts to the volume increasing stroke. Therefore, the refrigerant gas in the suction chamber 27 is sucked into the compression chamber 26 through the introduction chamber 36 of the rotary valve 35, the suction guide hole 37, and the conduction path 18 of the cylinder block 11 in the same order. The point in time when the suction guide hole 37 starts to communicate with the conduction path 18 (the compression chamber 26) is during the process of increasing the volume of the compression chamber 26.
[0050]
At the end of the volume increasing stroke of the compression chamber 26 (when the piston 24 is located at the bottom dead center), the suction guide hole 37 is completely displaced in the circumferential direction with respect to the conduction path 18, and The suction of the refrigerant gas into 26 is stopped. When the compression chamber 26 is shifted to the volume reduction stroke, the space between the conduction path 18 and the introduction chamber 36 is kept closed by the sealing area of the outer peripheral surface 35b of the rotary valve 35, and the compression of the refrigerant gas and the compression of the compressed gas are performed. The discharge to the discharge chamber 28 is not hindered.
[0051]
In the present embodiment, in the rotary valve 35, the seal area of the outer peripheral surface 35b that closes the conduction path 18 and the suction guide hole 37 that opens the conduction path 18 to the introduction chamber 36 constitute a first suction valve. are doing. In particular, the suction guide hole 37 can be understood as a first port of the first suction valve.
[0052]
Next, a description will be given of a suction timing adjustment mechanism (a suction timing adjustment passage and a suction timing adjustment valve) for always ensuring an optimal suction start timing in the suction of the refrigerant gas from the suction chamber 27 to the compression chamber 26.
[0053]
As shown in FIGS. 1 and 2, in the introduction chamber 36 of the rotary valve 35, a part of the outer peripheral wall 39 of the rotary valve 35 in the circumferential direction is padded inward, and a valve housing 41 is formed. It is projected. The valve housing 41 extends from the inner bottom surface of the introduction chamber 36 to the open end of the rotary valve 35. In the valve accommodating portion 41, a valve accommodating hole 42 having a bottomed cylindrical shape extending along the direction of the axis L of the rotary valve 35 is formed.
[0054]
The rear end side of the valve housing hole 42 is opened to the suction chamber 27 at the open end of the rotary valve 35. The inner space of the valve housing hole 42 is closed by a plug 43 inserted and fixed to the opening end side of the valve housing hole 42. The plug 43 is provided with a valve hole 43 a that communicates the suction chamber 27 with the inner space of the valve housing hole 42. The opening on the inner space side of the valve housing hole 42 in the valve hole 43 a is arranged on the inner end surface 43 b of the plug 43. A step 42a is provided on the inner peripheral surface near the center in the inner space of the valve accommodating hole 42 by setting a diameter difference such that the diameter of the plug 43 becomes larger.
[0055]
A columnar poppet 44 is housed in the valve housing hole 42. The poppet 44 is in contact with the inner end surface 43b of the plug 43 with the tip end surface 44a to close the valve hole 43a (see FIG. 1), and the outer peripheral edge of the back surface 44b is in contact with the wall surface of the step portion 42a to close the valve hole. It is slidable between a position (see FIG. 3) where the 43a is opened (fully opened). That is, the front end surface 44a of the poppet 44 forms a sealing surface, and the inner end surface 43b of the plug 43 forms a valve seat surface.
[0056]
The sliding movement of the poppet 44 described above is performed at the eccentric position of the rotary valve 35 and along the direction of the axis L of the rotary valve 35. That is, the poppet 44 is eccentrically arranged with respect to the axis L such that the center axis (hereinafter, simply referred to as the axis) S of the cylinder is parallel to the axis L of the rotary valve 35. More specifically, the poppet 44 has an axis L with respect to a plane orthogonal to the axis L with a plane including the axis L of the rotary valve 35 and the central axis P (hereinafter simply referred to as the axis) of the piston 24 at the top dead center position. It is eccentrically arranged so that the axis S is shifted to the P side.
[0057]
Due to the arrangement of the poppet 44 in the valve accommodating hole 42, the back pressure chamber 45 is connected to the left side of FIG. 1 which is the back surface 44b of the poppet 44 and to the right side of FIG. The chambers 46 are respectively defined. On the rear end side of the outer peripheral wall 39 of the rotary valve 35, a communication hole 47 is formed so as to penetrate in the radial direction of the rotary valve 35. The inner end of the communication hole 47 is opened near the plug 43 on the inner peripheral surface of the valve housing hole 42. In a state where the poppet 44 contacts the wall surface of the step portion 42a and opens the valve hole 43a, the inner end of the communication hole 47 is directly opened to the communication chamber 46, and the communication chamber 46 is connected to the valve hole 43a, that is, the suction chamber 27. Communicated through
[0058]
The outer end of the communication hole 47 is opened at the outer peripheral surface 35b of the rotary valve 35, and the opening position is a seal area facing the conduction path 18 to the compression chamber 26 immediately before the end of the volume reduction stroke. I have. That is, the point in time when the communication hole 47 starts to communicate with the conduction path 18 to the compression chamber 26 is during the stroke of reducing the volume of the compression chamber 26 (in this embodiment, immediately before the end of the stroke). Accordingly, when the piston 24 is located at the top dead center, the communication hole 47 has already started communicating with the conduction path 18 to the compression chamber 26 corresponding to the piston 24. That is, the communication hole 47 is communicated with the conduction path 18 to the compression chamber 26 in the volume increasing stroke before the suction guide hole 37.
[0059]
In the present embodiment, the valve hole 43a, the communication chamber 46, and the communication hole 47 have a first end that is always in communication with the suction chamber 27, and a second end that is in communication with the compression chamber 26 that is in a volume increasing stroke. A suction timing adjustment passage which communicates with the suction guide hole before the suction guide hole 37 is formed. In particular, the valve hole 43a (specifically, the opening end on the suction chamber 27 side) forms a first end of the suction timing adjustment passage, and the communication hole 47 (specifically, the outer end) forms a second end of the suction timing adjustment passage. .
[0060]
A gap (diameter difference) is set between the outer peripheral surface of the poppet 44 and the inner peripheral surface of the valve housing hole 42. The communication hole 47 and the back pressure chamber 45 are always in communication via a gap between the poppet 44 and the valve housing hole 42. Therefore, in a state where the communication hole 47 is communicated with the communication path 18 to the compression chamber 26, the pressure of the compression chamber 26 is increased through the communication hole 47 and the gap between the poppet 44 and the valve housing hole 42. 45.
[0061]
An urging spring 48 composed of a coil spring is interposed between the inner bottom surface and the back surface 44b of the poppet 44 in the valve accommodating hole 42. A region (small diameter portion) in the valve housing hole 42 on the front side of the step portion 42a also functions as a guide portion for guiding the fixed end side of the biasing spring 48 to stabilize the posture of the biasing spring 48. The biasing spring 48 biases the poppet 44 toward the stopper 43, that is, in a direction to close the valve hole 43a.
[0062]
The position of the poppet 44, that is, the opening or closing of the valve hole 43a by the poppet 44 is determined by the urging force of the urging spring 48 in the valve closing direction and the pressure of the back pressure chamber 45 acting on the back surface 44b in the valve closing direction. It is determined by the balance between the force and the force in the valve opening direction based on the pressure in the valve hole 43a (the suction chamber 27) acting on the distal end face 44a and acting against the force.
[0063]
As the urging spring 48, an extremely weak spring force is used. Therefore, if the pressure in the valve hole 43a slightly exceeds the pressure in the back pressure chamber 45, the poppet 44 seated on the inner end face 43b of the plug 43 is immediately separated from the inner end face 43b and is stepped away from the step 42a. Move to the position where it touches. If the pressure in the back pressure chamber 45 slightly exceeds the pressure in the communication chamber 46 in the open state of the valve hole 43a, the poppet 44 quickly separates from the stepped portion 42a and moves to the inner end surface 43b of the plug 43. It sits down and closes the valve hole 43a.
[0064]
In the present embodiment, the valve housing 41, the valve housing hole 42, the valve hole 43a, the poppet 44, the back pressure chamber 45, the communication chamber 46, the communication hole 47, the urging spring 48, and the like are formed of a differential pressure valve. It constitutes a timing control valve (second suction valve). In particular, the poppet 44 can be grasped as the valve body of the suction timing adjustment valve, and the communication hole 47 can be grasped as the second port of the second suction valve.
[0065]
As described above, the communication hole 47 of the rotary valve 35 is communicated with the conduction path 18 to the compression chamber 26 in the volume increasing step before the suction guide hole 37. In this state, if the pressure in the compression chamber 26 is higher than the pressure in the suction chamber 27, in other words, if the suction start timing is too early, the poppet 44 will apply a force based on the pressure in the back pressure chamber 45. The closed state of the valve hole 43a is maintained by the urging force of the urging spring 48 (see FIG. 1). Accordingly, the suction start timing is delayed, during which time the pressure in the compression chamber 26 decreases due to the increase in the volume of the compression chamber 26. As a result, when the communication between the compression chamber 26 and the suction chamber 27 is started, the backflow of the refrigerant gas from the compression chamber 26 to the suction chamber 27 can be suppressed.
[0066]
Conversely, in a state where the communication hole 47 is communicated with the communication path 18 to the compression chamber 26 in the volume increasing stroke prior to the suction guide hole 37, the pressure of the compression chamber 26 is reduced to the pressure of the suction chamber 27. If it is lower, the poppet 44 immediately opens the valve hole 43a by a force based on the pressure of the suction chamber 27 acting via the valve hole 43a (see FIG. 3). Therefore, it is possible to suppress the timing of starting the suction of the refrigerant gas from the suction chamber 27 into the compression chamber 26 from being delayed from the optimum suction start timing, and to suppress the rapid flow of the refrigerant gas from the suction chamber 27 into the compression chamber 26. it can.
[0067]
In the present embodiment, the communication hole in the outer peripheral surface 35b of the rotary valve 35 is such that the suction of the refrigerant gas from the suction chamber 27 into the compression chamber 26 is started by the opening of the valve hole 43a by the poppet 44. The arrangement position and arrangement region (opening region) of the opening 47 and the arrangement position and arrangement region (opening region) of the opening of the suction guide hole 37 are set.
[0068]
Further, in the present embodiment, the suction of the refrigerant gas from the suction chamber 27 into the compression chamber 26 is configured so as not to be interrupted in the course of the transfer of the communication with the conduction path 18 from the communication hole 47 to the suction guide hole 37. ing. That is, the circumferential distance between the opening of the communication hole 47 and the opening of the suction guide hole 37 on the outer peripheral surface 35b of the rotary valve 35 is such that both openings communicate with the same conduction path 18 (in other words, the same compression chamber 26) at the same time. Is set smaller than the maximum circumferential width of the opening of the conduction path 18 (the opening on the inner peripheral surface 17a of the housing hole 17).
[0069]
The present embodiment having the above configuration has the following operation and effects.
(1) By providing the suction timing adjusting mechanism, the suction start timing can be adjusted according to the operating conditions of the compressor 10. Therefore, for example, it is possible to effectively suppress occurrence of abnormal noise and the like, as compared with the technique of Patent Document 1 in which the inhalation start timing cannot be adjusted.
[0070]
(2) It is sufficient for the suction timing adjustment mechanism to appropriately adjust the suction start timing, and the main refrigerant gas is introduced from the suction chamber 27 to the compression chamber 26 through the suction guide hole 37. Accordingly, the maximum distance of the poppet 44 from the seated position on the stopper 43 may be small, and the problem of self-excited vibration of the poppet 44 due to the use of the differential pressure valve can be avoided.
[0071]
(3) For example, in a variable displacement swash plate type compressor in which a rotary valve is not used as a suction valve, a suction valve having a differential pressure valve is used to increase a suction flow rate of the refrigerant gas into the compression chamber when the inclination angle of the swash plate is large. It is necessary to increase the opening of the valve. That is, it is necessary to increase the amount by which the valve element of the suction valve can be separated from the seating position to the maximum (the amount by which the valve element moves from the seating position until it comes into contact with the stopper). For this reason, when the inclination angle of the swash plate is small, the flow rate of the refrigerant gas into the compression chamber is small, so that the valve body does not come into contact with the stopper and self-excited vibration is likely to occur.
[0072]
However, in the present embodiment, as described above, the amount of movement of the poppet 44 from the position where the poppet 43 is seated on the stopper 43 to the time when the poppet 44 comes into contact with the wall surface of the step portion 42a serving as a stopper is small. Therefore, even when the inclination angle of the swash plate 21 is small, when the refrigerant gas in the suction chamber 27 flows into the compression chamber 26 through the valve hole 43a, the communication chamber 46, and the communication hole 47, the poppet 44 is moved to the wall surface of the step portion 42a. And the poppet 44 does not cause self-excited vibration.
[0073]
(4) The point in time when the communication hole 47 starts to communicate with the compression chamber 26 is during the volume reduction stroke of the compression chamber 26. Therefore, even if the optimal suction start timing of the refrigerant gas from the suction chamber 27 to the compression chamber 26 comes immediately after the compression chamber 26 shifts from the volume reduction stroke to the volume increase stroke, the poppet 44 and the suction chamber 27 compress the refrigerant gas. The space with the chamber 26 can be immediately opened. Therefore, it is possible to more effectively suppress the delay of the suction start timing from the optimum suction start timing, and the refrigerant gas from the suction chamber 27 to the compression chamber 26 at the time when the communication between the compression chamber 26 and the suction chamber 27 starts. Can be more effectively prevented.
[0074]
(5) The poppet 44 is arranged at a position shifted from the axis L of the rotary valve 35. Therefore, the outer peripheral surface 35b of the rotary valve 35 is strongly pressed around the opening of the conduction path 18 on the side where the poppet 44 is displaced and disposed by the biasing effect of the centrifugal force, so that the seal is ensured.
[0075]
In particular, in the present embodiment, the poppet 44 has an axis S on the side of the axis P with a plane orthogonal to the axis L intersecting a plane including the axis L of the rotary valve 35 and the axis P of the piston 24 at the top dead center. Are eccentrically arranged so as to shift. Accordingly, the outer peripheral surface 35b of the rotary valve 35 is strongly pressed around the opening of the conduction path 18 to the compression chamber 26 at the latter stage of the volume reduction stroke due to the biasing effect of the centrifugal force. Leakage, that is, compression leakage can be reliably prevented. This leads to an improvement in the performance of the compressor 10.
[0076]
(6) In the suction timing adjusting valve formed of a poppet valve, self-excited vibration of the valve body (poppet 44) is less likely to occur as compared with a valve formed of a reed valve, for example.
(7) The poppet 44 opens and closes the valve hole 43a by sliding along the axis L of the rotary valve 35. Therefore, it is easy to realize a configuration in which the rotary valve 35 is provided with the suction timing adjusting valve formed of a poppet valve. In other words, the inside of the rotary valve 35 is more strict in space in the radial direction than in the direction of the axis L, while the poppet valve requires a large arrangement space in the moving direction of the poppet 44 (front and rear in the direction of the axis S).
[0077]
○ 2nd embodiment
As shown in FIG. 4, in the present embodiment, the first embodiment is changed, and no gap is set between the outer peripheral surface of the poppet 44 and the inner peripheral surface of the valve housing hole 42. The opening area of the conduction path 18 in the inner peripheral surface 17 a of the accommodation hole 17 is extended to the vicinity of the outer periphery of the back pressure chamber 45. The outer peripheral wall 39 of the rotary valve 35 is provided with a hole 61 communicating with the back pressure chamber 45 and opening to the outer peripheral surface 35b of the rotary valve 35. The hole 61 starts to communicate with the same conduction path 18 at substantially the same timing as the communication hole 47 and ends communication with the same conduction path 18 at substantially the same timing as the communication hole 47. Therefore, the pressure of the compression chamber 26 is introduced into the back pressure chamber 45 through the conduction path 18 and the hole 61.
[0078]
In the present embodiment having the above-described configuration, in addition to the same functions and effects as (1) to (7) of the first embodiment, the following functions and effects are achieved.
(8) The back pressure chamber 45 can communicate with the conduction path 18 through a dedicated passage (hole 61). Therefore, in the communication state between the conduction path 18 and the hole 61 and the communication hole 47, the pressure in the compression chamber 26 is directly reflected on the pressure in the back pressure chamber 45. Therefore, when the optimal inhalation start timing comes, the poppet 44 moves quickly and opens the valve hole 43a with little delay from the timing, so that the actual inhalation start timing is delayed from the optimal inhalation start timing. Can be effectively suppressed also in terms of the response delay of the poppet 44.
[0079]
○ Third embodiment
5 to 8 show a third embodiment.
As shown in FIG. 5, in the present embodiment, the in-shaft passage 34 of the rotary shaft 16 and the communication hole 35c of the rotary valve 35 are omitted, and the bleed passage 31 extends from the crank chamber 15 to the cylinder block 11, the valve / port. It reaches the suction chamber 27 via the formed body 13 and the rear housing 14.
[0080]
As shown in FIG. 6, in the rotary valve 35 of the present embodiment, the overlay portion forming the valve accommodating portion 41 in the first embodiment is deleted, and the introduction chamber 36 of the rotary valve 35 is provided. Is formed in a columnar shape. Therefore, the inner peripheral surface 36 a of the introduction chamber 36 is constituted by the cylindrical inner surface of the outer peripheral wall (cylindrical wall) 39 of the rotary valve 35. The introduction chamber 36 also serves as the valve housing hole 42. The plug 43 (valve hole 43a; see FIG. 3) is omitted from the rotary valve 35.
[0081]
The introduction chamber 36 forms a part of a suction timing adjustment passage. In particular, an opening end of the introduction chamber 36 (the rotary valve 35) on the suction chamber 27 side forms a first end of the suction timing adjustment passage. A circlip 51 is attached in the introduction chamber 36 near the suction chamber 27.
[0082]
The introduction chamber 36 accommodates a poppet 50 having a cylindrical shape with a bottom. The poppet 50 is arranged such that the rear side (the right side in FIG. 5) is the bottom. The poppet 50 contacts (sits) the circlip 51 with the outer peripheral edge of the outer bottom surface (the position shown in FIG. 5), and the position where the poppet 50 contacts the inner bottom surface (stopper) of the introduction chamber 36 with the open end surface. 7 position). The sliding movement of the poppet 50 is performed while sliding on the inner peripheral surface 36a of the introduction chamber 36 with the outer peripheral surface 50a. That is, the outer peripheral wall 39 of the rotary valve 35 also serves as a cylindrical wall that slidably holds the poppet 50, and the axis S of the poppet 50 coincides with the axis L of the rotary valve 35.
[0083]
An inner end of the communication hole 47 is opened in an inner peripheral surface 36 a of the introduction chamber 36 in a region closer to the poppet 50 than the circlip 51. An inner end of the suction guide hole 37 is opened in an inner peripheral surface 36 a of the introduction chamber 36 in a region in the front and rear direction of the axis S across the circlip 51.
[0084]
FIGS. 8A and 8B show that the rotational movement of the rotary valve 35 is linearly developed, and the rotation of the suction guide hole 37 and the communication hole 47 around the axis L is replaced by a leftward movement. FIG.
[0085]
As shown by hatching in FIG. 8A, when the poppet 50 is moved to a position where the poppet 50 contacts the circlip 51, a part of the outer peripheral surface 50 a of the poppet 50 (hereinafter referred to as a first valve portion). 50a-1), the opening of the communication hole 47 to the introduction chamber 36 is closed. When the poppet 50 is moved to a position where it contacts the circlip 51, a portion (hereinafter, referred to as a second valve portion) 50a on the outer peripheral surface 50a of the poppet 50 that is different from the first valve portion 50a-1. By -2, the opening degree of the opening of the suction guide hole 37 with respect to the introduction chamber 36 is minimized, which is not zero.
[0086]
As shown in FIG. 8B, in a state where the poppet 50 has been moved to a position where it contacts the inner bottom surface of the introduction chamber 36, the first valve portion 50 a-1 of the poppet 50 introduces the communication hole 47. The opening to the chamber 36 is opened. In a state where the poppet 50 is moved to a position where the poppet 50 contacts the inner bottom surface of the introduction chamber 36, the second valve portion 50 a-2 of the poppet 50 adjusts the opening degree of the suction guide hole 37 with respect to the introduction chamber 36. Maximum (fully open).
[0087]
The outer peripheral wall 39 of the rotary valve 35 is provided with a hole 61 communicating with the back pressure chamber 45 and opening on the outer peripheral surface 35b of the rotary valve 35. A groove 60 extending forward from the communication hole 47 is formed in the outer peripheral surface 35 b of the rotary valve 35. The hole 61 communicates with the groove 60, and the hole 61 is opened in the back pressure chamber 45 on the bottom side of the introduction chamber 36. Therefore, in a state where the communication hole 47 is communicated with the conduction path 18 to the compression chamber 26, regardless of the position of the poppet 50, the same pressure in the compression chamber 26 is applied through the conduction path 18, the groove 60, and the hole 61. It is introduced into the pressure chamber 45.
[0088]
The position of the poppet 50, that is, the opening or closing of the communication hole 47 by the poppet 50, opposes the force in the valve closing direction based on the pressure of the back pressure chamber 45 acting on the open end face side of the poppet 50 and this force. And the force in the valve opening direction based on the pressure of the communication chamber 46 (suction chamber 27) acting on the outer bottom surface. In this embodiment, the biasing spring 48 provided in the first embodiment is omitted. Further, in the present embodiment, unlike the first embodiment, the suction of the refrigerant gas from the suction chamber 27 to the compression chamber 26 always starts by the opening of the communication hole 47 by the first valve portion 50a-1 of the poppet 50. It is not always set.
[0089]
In the present embodiment, the poppet 50, the back pressure chamber 45, the communication hole 47, the groove 60, the hole 61, and the like constitute a suction timing adjustment valve (second suction valve) composed of a differential pressure valve.
[0090]
In the present embodiment having the above configuration, in addition to the same functions and effects as (1) to (4) and (6) to (8) of the first and second embodiments, the following functions and effects are obtained. .
[0091]
(9) The poppet 50 is arranged such that the axis S of the poppet 50 matches the axis L of the rotary valve 35. Therefore, the rotation balance of the rotary valve 35 can be improved. Therefore, for example, as compared with the case where the axis L of the rotary valve 35 is displaced from the axis S of the poppet 50, the offset load acting on the rotary valve 35 due to the biasing effect of the centrifugal force can be reduced, and The durability of the valve 35 can be improved. In the rotary valve 35, a structure (cylindrical wall) for slidably holding the poppet 50 can be provided coaxially with the axis L. For example, when the structure is provided at a position deviated from the axis L The processing cost of the rotary valve 35 can be reduced as compared with the case of FIG.
[0092]
(10) The outer peripheral wall (cylindrical wall) 39 of the rotary valve 35 also serves as a cylindrical wall that slidably holds the poppet 50. Therefore, in the rotary valve 35, it is not necessary to provide a cylindrical wall for slidably holding the poppet 50 separately from the outer peripheral wall 39, and the processing cost of the rotary valve 35 can be further reduced. Further, since the introduction chamber 36 can be made large, the suction of the refrigerant gas from the suction chamber 27 to the compression chamber 26 through the suction guide hole 37 is performed smoothly, and the suction efficiency can be improved.
[0093]
(11) The poppet 50 is provided with a second valve portion 50a-2 for adjusting the opening degree of the suction guide hole 37, in addition to the first valve portion 50a-1 for opening and closing the communication hole 47.
The second valve portion 50a-2 increases the opening degree of the suction guide hole 37 with respect to the introduction chamber 36 when the first valve portion 50a-1 opens the communication hole 47. That is, for example, the second valve portion 50a-2 is in a state where the first valve portion 50a-1 opens the communication hole 47 when the communication between the suction guide hole 37 and the compression chamber 26 is started ( In a case where a suitable suction start timing has arrived or has already passed), the opening degree of the suction guide hole 37 with respect to the introduction chamber 36 is increased. Therefore, the suction of the refrigerant gas from the suction chamber 27 to the compression chamber 26 through the suction guide hole 37 is performed more smoothly, and the suction efficiency can be further improved.
[0094]
The second valve portion 50a-2 reduces the opening degree of the suction guide hole 37 with respect to the introduction chamber 36 when the first valve portion 50a-1 closes the communication hole 47. That is, for example, the second valve portion 50a-2 is in a state where the first valve portion 50a-1 closes the communication hole 47 at the time when the communication between the suction guide hole 37 and the compression chamber 26 is started ( Under a situation where a suitable suction start timing has not arrived), the opening degree of the suction guide hole 37 with respect to the introduction chamber 36 is reduced. Therefore, the reverse flow rate of the refrigerant gas from the compression chamber 26 to the suction guide hole 37 side can be reduced, and the generation of suction pulsation and a decrease in volumetric efficiency can be more effectively suppressed.
[0095]
In other words, in the present embodiment, by providing the poppet 50 with the second valve portion 50a-2, even with respect to "a large delay of a suitable suction start timing" which cannot be handled by the first valve portion 50a-1, It can be dealt with suitably.
[0096]
The above-mentioned “a situation where the first valve portion 50a-1 closes the communication hole 47 when the communication between the suction guide hole 37 and the compression chamber 26 is started” is, for example, the discharge capacity of the compressor. Is easy to fall when is low. When the discharge capacity of the compressor is low, the pulsation of the refrigerant gas is liable to propagate due to the low density of the refrigerant gas and the high dryness of the refrigerant gas. Therefore, it can be said that it is particularly effective to suppress the generation of the suction pulsation more effectively at the time of the low discharge capacity in which the pulsation is easily propagated.
[0097]
By the way, if a certain period of time elapses from the time when the communication between the suction guide hole 37 and the compression chamber 26 is started, the communication hole 47 preceding the suction guide hole 37 has a certain communication with the suction guide hole 37. It faces another compression chamber 26 different from the compression chamber 26 (see FIG. 6). Here, for example, when the discharge capacity of the compressor is low and the suitable suction start timing is greatly delayed, the first valve portion 50a-1 opens the communication hole 47 facing the certain compression chamber 26 described above. Without this, the communication hole 47 is shifted to a state in which it faces another compression chamber 26.
[0098]
That is, when the suitable suction start timing is greatly delayed, the communication hole 47 is always closed by the first valve portion 50a-1, and the opening degree of the suction guide hole 37 is changed to the second valve portion 50a-2. Will always be smaller. As a result, the refrigerant gas heading toward the compression chamber 26 via the suction guide hole 37 is throttled, and the refrigerant gas is rectified, so that the suction pulsation is effected over the entire period of the volume increasing stroke when the compressor has a low discharge capacity. Can be suppressed.
[0099]
○ Fourth embodiment
In the above embodiments, the poppet valve is used as the suction timing control valve. This is changed, and in the present embodiment, as shown in FIG. 9, a reed valve is used as a suction timing adjusting valve. The suction timing control valve formed of a reed valve has a simpler configuration than, for example, a poppet valve, which leads to a reduction in man-hours for manufacturing the suction timing control valve.
[0100]
To describe this embodiment in detail, a valve housing recess 65 is formed on the outer peripheral surface 35b of the rotary valve 35, and the inner space of the valve housing recess 65 and the introduction chamber 36 are communicated via a communication hole 66. I have. The valve housing recess 65 functions in the same manner as the communication hole 47 (see FIG. 2) in each of the above-described embodiments. Therefore, the opening 65a of the valve housing recess 65 is connected to the conduction path 18 to the compression chamber 26 in the volume increasing process. , And is communicated before the suction guide hole 37 (see FIG. 2). In the present embodiment, the valve housing recess 65, the communication hole 66, and the introduction chamber 36 form a suction timing adjustment passage. In particular, the introduction chamber 36 forms a first end of the suction timing adjustment passage, and the valve housing recess 65 forms a second end of the suction timing adjustment passage.
[0101]
A lead-type valve body 67 is housed in the valve housing recess 65, and the valve body 67 opens or opens the communication hole 66 according to the difference between the pressure in the introduction chamber 36 and the pressure in the valve housing recess 65. Close. The maximum opening degree of the valve body 67 is defined by the retainer 68 arranged in the valve housing recess 65. The valve body 67 has a very low spring force. Therefore, when the pressure in the introduction chamber 36 slightly exceeds the pressure in the valve housing recess 65, the valve body 67 quickly moves to a position where it comes into contact with the retainer 68 to open the communication hole 66. Further, in a state where the communication hole 66 is opened, if the pressure in the valve housing recess 65 slightly exceeds the pressure in the introduction chamber 36, the valve body 67 quickly closes the communication hole 66.
[0102]
In the present embodiment, the valve housing recess 65, the communication hole 66, the valve body 67, the retainer 68, and the like constitute a suction timing control valve (second suction valve) composed of a differential pressure valve. In particular, the valve housing recess 65 can be understood as a second port of the second suction valve. Also in the present embodiment, the same operation and effect as (1) to (5) of the first embodiment are exerted.
[0103]
It should be noted that, for example, the following embodiments can be implemented without departing from the spirit of the present invention.
In each of the above embodiments, the point in time when the communication hole 47 starts to communicate with the compression chamber 26 is during the volume reduction stroke of the compression chamber 26. By changing this, the time when the communication hole 47 starts to communicate with the compression chamber 26 is defined as the end of the volume reduction stroke of the compression chamber 26 (the time when the piston 24 is located at the top dead center). Even in this case, the same effect as (4) of the first embodiment can be obtained.
[0104]
In each of the above embodiments, the point in time when the communication hole 47 starts to communicate with the compression chamber 26 is during the volume reduction stroke of the compression chamber 26. By changing this, the time when the communication hole 47 starts to communicate with the compression chamber 26 is set to a time earlier than the time when the suction guide hole 37 starts to communicate with the compression chamber 26 during the process of increasing the volume of the compression chamber 26. And
[0105]
In the above embodiments, the circumferential distance between the opening of the communication hole 47 and the opening of the suction guide hole 37 on the outer peripheral surface 35b of the rotary valve 35 is such that both openings communicate with the same conduction path 18 at the same time. As a result, the width is set to be smaller than the maximum width in the circumferential direction at the opening of the conduction path 18 (the opening at the inner peripheral surface a of the housing hole 17). By changing this, the circumferential distance between the opening of the communication hole 47 and the opening of the suction guide hole 37 is made larger than the maximum width of the opening of the conduction path 18, so that both openings communicate with the same conduction path 18 at the same time. To prevent a condition from being brought about.
[0106]
In each of the above embodiments, the passage that connects the suction guide hole 37 and the communication hole 47 to the compression chamber 26 is the one conduction passage 18 that is shared between the two 37 and 47. This is changed, and a passage for communicating the communication hole 47 with the compression chamber 26 is provided in the cylinder block 11 independently of the conduction passage 18. In this case, the opening of the communication hole 47 in the outer peripheral surface 35b of the rotary valve 35 is arranged to be shifted from the opening of the suction guide hole 37 in the direction of the axis L.
[0107]
In the third embodiment, an urging spring for urging the poppet 50 toward the suction chamber 27 is provided in the back pressure chamber 45, that is, between the inner bottom surface of the introduction chamber 36 and the inner bottom surface of the poppet 50. May be provided.
[0108]
In the third embodiment, the outer peripheral wall 39 of the rotary valve 35 also serves as a cylindrical wall that slidably holds the poppet 50. By changing this, a cylindrical wall dedicated to the poppet 50 is provided on the rotary valve 35 separately from the outer peripheral wall (cylindrical wall) 39 at a position coaxial with the outer peripheral wall 39. That is, the rotary valve 35 has a double cylindrical structure including the outer peripheral wall 39 on the outside and the cylindrical wall for poppet holding disposed inside the outer peripheral wall 39.
[0109]
In the third embodiment, the poppet 50 also adjusts the opening of the suction guide hole 37. This is changed so that the poppet 50 does not participate in the adjustment of the opening degree of the suction guide hole 37 even when the poppet 50 slides. For example, in the third embodiment, the suction guide hole 37 and the communication hole 47 are disposed so as to overlap with each other in the direction of the axis S, but this is changed so that the communication hole 47 is located forward of the suction guide hole 37. And the circlip 51 is disposed forward of the suction guide hole 37.
[0110]
The fourth embodiment is modified such that a portion that opens and closes the communication hole 66 in the valve body 67 is a first valve portion, and the valve body 67 is provided with a second valve portion that adjusts the opening degree of the suction guide hole 37. thing. In this case, the same operation and effect as (11) of the third embodiment can be obtained.
[0111]
The present invention may be applied to a wobble type variable displacement compressor.
The present invention may be applied to a double-headed piston type compressor.
The present invention may be applied to a wave cam type piston compressor.
[0112]
The technical idea that can be grasped from the above embodiment will be described.
(1) A conduction path extending from the compression chamber, which communicates the suction guide passage with the compression chamber, is opened to face an outer peripheral surface of the rotary valve, and a valve body of the suction timing control valve is connected to the rotary valve of the rotary valve. The piston type compressor according to claim 1, wherein the piston type compressor is arranged at a position shifted from a rotation center axis.
[0113]
(2) The suction timing adjusting valve is a poppet valve, and the poppet provided in the poppet valve is a rotary valve with respect to a plane including the center axis of rotation of the rotary valve and the center axis of the piston at the top dead center position. The piston-type compressor according to the above technical concept (1), wherein the piston-type compressor is eccentrically arranged on the center axis side of the piston with respect to a plane orthogonal to the rotation center axis of the piston.
[0114]
(3) The second end of the suction timing adjustment passage and the suction guide passage are configured to be brought into a state where they are simultaneously communicated with the same compression chamber. The piston type compressor according to the concept (1) or (2).
[0115]
(4) A cam plate for converting the rotational movement of the rotary shaft into a reciprocating motion of a piston, wherein a displacement of the piston can be changed by changing a tilt angle of the cam plate to change a displacement of the piston. The piston type compressor according to any one of claims 1 to 8, or any one of the technical ideas (1) to (3).
[0116]
【The invention's effect】
ADVANTAGE OF THE INVENTION According to this invention of the said structure, in a piston type compressor using a rotary valve as a suction valve, the suction start timing can be adjusted according to the operating conditions of this piston type compressor, and generation of abnormal noise is effective. Can be suppressed.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a variable displacement swash plate type compressor.
FIG. 2 is a sectional view taken along line 1-1 of FIG. 1;
FIG. 3 is an enlarged sectional view of a main part showing an opened state of a suction timing control valve.
FIG. 4 is an enlarged sectional view of a main part showing a second embodiment.
FIG. 5 is a sectional view of a main part showing a third embodiment.
FIG. 6 is a sectional view taken along line 2-2 of FIG. 5;
FIG. 7 is an enlarged sectional view of a main part showing an open state of the suction timing control valve.
8A and 8B are diagrams showing the rotary movement of the rotary valve in a linearly developed manner, wherein FIG. 8A shows a closed state of the suction timing control valve, and FIG. 8B shows an open state of the suction timing control valve.
FIG. 9 is an enlarged sectional view of a main part showing a fourth embodiment.
[Explanation of symbols]
Reference numeral 10: Variable displacement swash plate type compressor as a piston type compressor, 16 ... Rotary shaft, 23 ... Cylinder bore, 24 ... Piston, 26 ... Compression chamber, 27 ... Suction chamber constituting suction pressure region, 35 ... Rotor Rotary valve, 35b: outer peripheral surface of rotary valve constituting first suction valve, 36: introduction chamber (constituting suction timing adjustment passage in the third and fourth embodiments), 36a: introduction of cylindrical inner surface of outer peripheral wall An inner peripheral surface of the chamber, 37: a suction guide hole constituting a first suction valve and serving as a first port of the valve; a suction guide hole as a suction guide passage; 39, an outer peripheral wall of a rotary valve; 43a: a suction timing adjustment passage; Valve holes 44, 50 (50 are shown in the third embodiment) constituting a suction timing control valve; poppets constituting a suction timing control valve (second suction valve) and being a valve body of the valve; ... Communication chambers forming suction timing control passages and suction timing control valves, 47 communication holes forming suction timing control passages and suction timing control valves and serving as second ports, 50a-1. Portion (third embodiment), 50a-2: second valve portion of valve body (third embodiment), 65: valve housing concave portion (fourth embodiment) forming suction timing adjustment passage, 66 ... communication hole similarly (Fourth embodiment), 67: valve body of suction timing control valve (fourth embodiment), L: center axis of rotation of rotary valve, S: center axis of poppet.

Claims (9)

A rotary valve having a suction guide passage for accommodating a piston in a plurality of cylinder bores arranged around the rotation axis and for introducing gas from a suction pressure region into a compression chamber defined by the piston in the cylinder bore; A piston-type compressor that introduces gas from the suction pressure region to the compression chamber through the suction guide passage by communication between the compression chamber and the suction guide passage;
A suction timing adjustment passage is formed in the rotary valve, and a first end of the suction timing adjustment passage is always in communication with the suction pressure region, and a second end of the suction timing adjustment passage is in a volume increasing stroke. The suction chamber is communicated with the compression chamber ahead of the suction guide passage, and a suction timing adjustment valve is provided on the suction timing adjustment passage in the rotary valve. The suction timing adjustment passage is opened or closed according to a difference between a force based on the pressure on the suction pressure region side acting in the opening direction and a force based on the pressure on the compression chamber side acting in the valve closing direction. Piston type compressor. 2. The piston type according to claim 1, wherein a point in time at which communication between the second end of the suction timing adjustment passage and the compression chamber is started is during a volume reduction stroke of the compression chamber or at an end of the volume reduction stroke. Compressor. 3. The piston type compressor according to claim 1, wherein the suction timing control valve is a poppet valve. The piston type compression according to claim 3, wherein a poppet as a valve body provided in the suction timing adjustment valve is configured to be able to open and close a suction timing adjustment passage by sliding along a rotation center axis of the rotary valve. Machine. The piston type compressor according to claim 4, wherein the poppet is arranged such that a center axis of the poppet coincides with a rotation center axis of the rotary valve. The piston type compressor according to claim 5, wherein the poppet is slidably arranged on the rotary valve with respect to a cylindrical inner surface of an outer peripheral wall provided in the rotary valve. 3. The piston type compressor according to claim 1, wherein the suction timing adjusting valve is a reed valve. The valve body included in the suction timing adjustment valve includes a second valve portion that adjusts an opening degree of the suction guide passage, in addition to a first valve portion that opens and closes the suction timing adjustment passage. The second valve portion increases the opening of the suction guide passage when the first valve portion opens the suction timing adjustment passage, and increases the opening degree of the suction guide passage when the first valve portion closes the suction timing adjustment passage. The piston type compressor according to any one of claims 1 to 7, wherein an opening degree of the suction guide passage is reduced. In a piston type compressor provided with a first suction valve that opens and closes a gas passage between a suction pressure region and a compression chamber in synchronization with rotation of the rotation shaft, on a rotor that rotates in synchronization with rotation of the rotation shaft,
The rotor is provided with a second suction valve, and the second suction valve communicates with a compression chamber in a volume increasing stroke prior to a first port provided in the first suction valve. The second suction valve has a force based on the pressure in the suction pressure region acting in the valve opening direction and a force based on the pressure in the compression chamber acting in the valve closing direction. A piston-type compressor that opens or closes between the second port and the suction pressure region according to the difference between the two.

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