JP2006170087A - Mechanism of supplying refrigerant gas from suction pressure space of compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To achieve high efficiency of a piston type swash plate compressor at the time of both high rotation and low rotation of the compressor when supplying refrigerant gas from a suction pressure space into a cylinder bore working chamber. <P>SOLUTION: At the time of low rotation of the compressor 1, a flapper valve 31 is switched to operate for supplying the refrigerant gas from a suction chamber 12 into the cylinder bore working chamber 27 via a suction passage 30 because the efficiency of the flapper valve 31 is high. At the time of high rotation of the compressor 1, a rotary valve 36 is switched to operate for supplying the refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27 via a suction passage 35 because the efficiency of the rotary valve 36 is high. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a mechanism for supplying refrigerant gas from a suction pressure space into a cylinder bore working chamber, for example, a swash plate type piston compressor used in an air conditioner for vehicles.

  As a kind of the swash plate type piston type compressor used for this kind of vehicle air conditioner, the electric piston type compressor which drives a drive shaft with an electric motor as shown in patent documents 1, and patent documents 2 are mentioned. There is already a belt-driven piston compressor that drives the drive shaft by projecting the tip of the drive shaft as shown in the figure and connecting the tip of the drive shaft and a pulley and interlocking them via an engine and a belt. It is known.

  Of these, in the compressor described in Patent Document 1, a suction port that is defined in the rear side member and communicates with the evaporator is connected as a mechanism for supplying refrigerant gas from the suction chamber to the cylinder bore working chamber. A suction hole formed in a valve plate communicating with the suction chamber and the cylinder bore working chamber, and a suction valve (flapper valve type) provided on the front side end face of the valve plate for opening and closing the suction hole. Are shown).

Further, in the compressor described in Patent Document 2, as the refrigerant gas suction guide mechanism, a rotary valve is disposed on the rear side in the axial direction of the drive shaft, and this rotary valve is opposite to the drive shaft in the axial direction. A suction opening that opens to the side of the cylinder bore and communicates with the cylinder bore working chamber when the rotary valve is in a predetermined rotational position by bending in the radial direction of the rotary valve in the middle after extending along the axial direction of the rotary valve. A passage is formed.
Japanese Patent Laid-Open No. 2001-200785 Japanese Patent Laid-Open No. 5-164044

  However, in the structure of the mechanism for supplying the refrigerant gas from the suction chamber to the cylinder bore working chamber as shown in Patent Document 1, since only the flapper valve is used as the type of the suction valve, it is higher than that at the time of low rotation of the compressor. There is a problem that the efficiency of the compressor is lowered because a valve response delay or the like occurs during rotation.

  Further, in the refrigerant gas suction guide mechanism that supplies the refrigerant gas from the suction chamber to the cylinder bore working chamber shown in Patent Document 2, only the rotary valve is used as the type of the suction valve. If the valve opening / closing timing and valve shape are determined so that the efficiency is high, the optimal efficiency of the compressor cannot be improved when the compressor is running at low speed. Has the problem of having to allow.

  Therefore, the present invention provides a compressor capable of obtaining high efficiency of the compressor both when the compressor is rotating at a high speed and a low speed when supplying the refrigerant gas from the suction pressure space to the cylinder bore working chamber. An object of the present invention is to provide a refrigerant gas supply mechanism from the suction pressure space.

  The refrigerant gas supply mechanism from the suction pressure space of the compressor according to the present invention includes a drive shaft that passes through the crank chamber and is rotatably supported by the casing, and is disposed in the crank chamber and is synchronized with the rotation of the drive shaft. A swash plate type piston-type compression comprising at least a swash plate that rotates, a piston that reciprocally slides in a cylinder bore as the swash plate rotates, and a suction pressure space defined in a rear side member that constitutes the casing. In the machine, a first suction passage that directly communicates the suction pressure space and the cylinder bore working chamber is provided, a flapper valve that opens and closes the first suction passage is disposed, and the drive shaft has a rear side member side. A rotary valve is configured by providing a second suction passage at one end and one end communicating with the suction pressure space and the other end intermittently communicating with the cylinder bore working chamber. It is characterized in that the valve mechanism for opening and closing the for the suction opening is provided at one inlet opening end side of the second suction passage constituting the rotary valve (claim 1). Of these, the swash plate type piston type compressor may be either an electric type using a built-in electric motor or a belt drive type, and may be either a fixed capacity type or a variable capacity type. Further, it may be any of a swash plate type, a wobble plate type, a single side swash plate type, and a double swash plate type. The suction pressure space is not limited to the suction chamber, and may be, for example, a motor chamber having the same pressure as the suction chamber. Furthermore, the valve mechanism is not limited to the case where there are six cylinder bores, for example, and may be provided only in three of the six cylinder bores. The valve mechanism is opened by utilizing centrifugal force or other external input due to the rotation of the drive shaft, and the valve mechanism is closed by utilizing a biasing force (restoring force) by an elastic member. The material, shape, number, and mounting position of each member such as a valve body and an elastic member that constitute the member are not particularly limited, but the following can be exemplified.

  That is, the valve mechanism is configured to have a thin plate portion that is swingably provided in the vicinity of the suction opening formed on the side surface of the rotary valve, so that the spring force of the thin plate portion is reduced when the compressor rotates at a low speed. The suction opening is closed, and the suction opening of the rotary valve is separated from the suction opening of the rotary valve against the spring force of the thin plate portion using centrifugal force when the compressor rotates at high speed. (Claim 2).

  The valve mechanism includes a valve seat having a passage communicating with a passage having a suction opening portion of the second suction passage, and one of the axial directions is closed by a closing portion, and the valve seat is closed on the other opening side. A cover to be joined, a through-hole opened in a side surface of the cover, a valve body that is movable along the axial direction of the cover, and an elastic member that is disposed on the closing part side with respect to the valve body And the through hole of the cover body can communicate with the suction opening of the rotary valve, and the urging force of the elastic member against the valve body is larger than the centrifugal force at the time of low rotation of the compressor The compressor is set to be smaller than the centrifugal force at the time of high rotation (Claim 3).

  The valve mechanism according to claim 3 may be configured such that the valve mechanism includes a magnet disposed on the closing portion side of the cover, and the valve body is formed of a material that can be attracted to the magnet. 4).

  Further, the valve mechanism includes a valve seat having a passage communicating with a passage having the suction opening portion of the second suction passage, and one of the axial directions is closed by the closing portion and the valve seat is closed on the other opening side. A cover to be joined, a through-hole opened in a side surface of the cover, a valve body that is movable along the axial direction of the cover, and an elastic member that is disposed on the closing part side with respect to the valve body And an electromagnetic coil formed by winding an electric wire on the radially outer side of the valve body to which a voltage is applied, and the through hole of the cover body can communicate with the suction opening of the rotary valve The valve body closes the through hole by the biasing force of the elastic member against the valve body, and the valve body is applied to the biasing force of the elastic member by applying a voltage to the electromagnetic coil. For example, it is attracted to the closed side of the cylindrical body to open the through hole. That (claim 5). This valve mechanism may be provided with a suction opening provided on the side surface of the rotary valve and attached to the suction opening as in the valve mechanism according to any one of claims 1 to 4, or the axial end of the rotary valve. An inhalation opening may be provided in the part and attached to the inhalation opening.

  According to these inventions, since the efficiency of the flapper valve is good at the time of low rotation of the compressor, the flapper valve is operated to supply the refrigerant gas from the suction pressure space into the cylinder bore working chamber through the first suction passage, Since the efficiency of the rotary valve is good at the time of high rotation of the compressor, the rotary valve is operated so that the refrigerant gas is supplied from the suction pressure space mainly into the cylinder bore working chamber through the second suction passage. Therefore, it is possible to keep the efficiency of the compressor relatively high regardless of the rotation speed range of the compressor.

  That is, for example, in the case of an electric compressor, the compression efficiency characteristic that is generally deteriorated at high rotation can be improved by using only a flapper valve, and in the case of a belt-driven compressor, for example, it is low by using only a rotary valve. The compression efficiency characteristic that the efficiency of the compressor is reduced during rotation can be improved, and the efficiency during idling can be improved.

  Particularly, in the valve mechanism described in claim 4, it is possible to relatively clarify the operation switching of the valve mechanism, and in the valve mechanism described in claim 5, the operation switching of the valve mechanism is relatively relative. It is possible to arbitrarily control the rotational speed of the compressor at the time of switching.

  Embodiments of the present invention will be described below with reference to the drawings.

  In FIG. 1, an electric compressor 1 is shown as an example of a piston-type swash plate compressor in which the present invention is used. The compressor 1 is used in a vehicle air conditioner and constitutes a part of a known refrigeration cycle. That is, the compressor 1 compresses the refrigerant gas that has been reduced in temperature and pressure by an evaporator (not shown) to increase the temperature and pressure, and sends the compressed refrigerant gas to a condenser (not shown).

  The configuration of the compressor 1 will be described. A cylinder block 2, a front side member 3 fixed to the front side of the cylinder block 2, a rear side member 4 fixed to the rear side of the cylinder block 2, and the front A motor housing member 5 that is disposed further on the front side than the side member 3 and houses an electric motor 20 to be described later, and a drive shaft 14 are provided. These cylinder block 2, front side member 3, rear side member 4, and motor housing are provided. The member 5 constitutes a substantially cylindrical casing 1a by inserting a plurality of fastening bolts (not shown) along the axial direction of the cylinder bore and joining and fixing them.

  Then, the motor chamber 8 is defined by joining the front side member 3 and the motor housing member 5 via the plate 7, and the crank chamber 9 is defined by joining the front side member 3 and the cylinder block 2. Further, the suction chamber 12 and the discharge chamber 13 are defined in the rear side member 4 by joining the cylinder block 2 and the rear side member 4 via the plate 11.

  The suction chamber 12 is for containing the refrigerant gas supplied to the cylinder bore working chamber 27, and is formed in the central portion of the rear side member 4, and communicates with a suction port 32 that leads to an outlet side of an evaporator (not shown). Communication with the cylinder bore working chamber 27 is possible. The discharge chamber 13 is for containing the refrigerant gas discharged from the cylinder bore working chamber 27, and is continuously formed around the suction chamber 12, and has a discharge port 33 leading to the inlet side of a condenser (not shown). The cylinder bore working chamber 27 can communicate with the cylinder bore.

  The drive shaft 14 extends from the motor housing member 5 through the plate 7, the crank chamber 9 of the front side member 3, and the cylinder block 2 to reach the suction chamber 12 of the rear side member 4. The motor housing member 5 is rotatably attached via a bearing mechanism 15 and a bearing mechanism 16 provided on the front side member 3. The rotational force with respect to the drive shaft 14 is applied by an electric motor 20 housed in the motor chamber 8, and the electric motor 20 includes a stator 18 and a rotor 19 that is rotatably attached to the drive shaft 14. It consists of

  The cylinder block 2 is formed with a plurality of cylinder bores 21 arranged at equal intervals on a circumference around the drive shaft 14 so as to surround the drive shaft 14. In each cylinder bore 21, a single-head piston 22 composed of a hollow head portion 22a and a tail portion 22b is inserted so as to be reciprocally slidable. A shoe receiving portion having a concave curved surface is formed opposite to the head portion 22a and the tail portion 22b of the one-head piston 22 in order to dispose the shoe 23.

  Furthermore, a thrust flange 24 that rotates integrally with the drive shaft 14 is fixed in the crank chamber 9 that communicates with the cylinder bore 21 of the cylinder block 2. The thrust flange 24 is rotatably supported via the bearing mechanism 25 with respect to the front side member 3. A swash plate 26 is integrally connected to the thrust flange 24, and the swash plate 26 rotates integrally with the rotation of the thrust flange 24. The swash plate 26 is moored to the tail portion 22b of the one-headed piston 22 via a pair of shoes 23 provided so that the peripheral edge portion is sandwiched between the front and rear.

  Accordingly, when the drive shaft 14 rotates, the swash plate 26 rotates accordingly, and the rotational motion of the swash plate 26 is converted into the reciprocating linear motion of the single-headed piston 22 via the shoe 23. Thus, the volume of the cylinder bore working chamber 27 formed between the single-headed piston 22 and the plate 11 in the cylinder bore 21 is changed.

  By the way, as a mechanism for supplying the refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27, the present invention includes the following two suction valve mechanisms. Among these, the first suction valve mechanism for supplying the refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27 corresponds to each cylinder bore 21 around the through hole 29 through which the drive shaft 14 of the plate 11 is inserted. The first suction passage 30 is formed, and the first suction passage 30 is opened and closed by a flapper valve 31 provided as a suction valve on the front side end surface of the plate 11. The flapper valve 31 is further a reed valve in this embodiment.

  The second suction valve mechanism for supplying the refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27 has one end communicating with the suction chamber 12 and the other end of the drive shaft 14 on the rear side member 4 side. Is provided as a rotary valve 36 by providing a second suction passage 35 intermittently communicating with the cylinder bore working chamber 27.

  That is, the rotary valve 36 has a passage 35a extending in the axial direction in the drive shaft 14 and a radial direction extending in the drive shaft 14 at a portion projecting into the suction chamber 12 of the drive shaft 14. A passage 35b having a suction opening communicating with 12 and a passage 35c extending radially in the drive shaft 14 at a portion substantially parallel to the cylinder bore of the drive shaft 14 and having a discharge opening. It has a letter shape and rotates integrally with the drive shaft 14 as a part of the drive shaft 14. As a result, the rotary valve 36 communicates intermittently with a passage 35 d in which the discharge opening is formed in the cylinder block 2.

  On the other hand, the mechanism for discharging the refrigerant gas from the cylinder bore working chamber 27 to the discharge chamber 13 forms a discharge passage 37 corresponding to the cylinder bore 21 in the plate 11, and this discharge passage 37 is provided on the rear side end face of the plate 11. The discharge valve 38 is opened and closed.

  As shown in FIGS. 2 and 3, a valve mechanism 39 for opening and closing the suction opening is disposed in the suction opening of the passage 35 b of the rotary valve 36. The valve mechanism 39 is a leaf spring / reed valve that also functions as a check valve (a check valve), and has a thin plate portion 40 having an arcuate inner peripheral surface having the same radius of curvature (R) as the side surface of the rotary valve 36. And one end in the circumferential direction of the thin plate portion 40 and the side surface of the rotary valve 36 are fixed by a fixing member 41 so as to be swingable. The other end in the circumferential direction of the thin plate portion 40 is directed outward. And a bent portion 42 formed by bending.

  The valve mechanism 39 closes the suction opening of the passage 35b by bringing the inner side surface of the thin plate portion 40 into close contact with the side surface of the rotary valve 36 as shown in FIG. As shown in FIG. 2B, the thin plate portion 40 swings from the state shown in FIG. 2A with the fixing member 41 as a fulcrum and moves away from the side surface of the rotary valve 36. Do.

  The external input applied to the valve mechanism 39 is the spring force of the thin plate portion 40 itself that the inner surface of the thin plate portion 40 tries to closely contact the side surface of the rotary valve 36 for closing the suction opening of the passage 35b. For opening the suction opening of the passage 35b, the resultant force is indicated by an arrow A in FIG.

  That is, when the rotary valve 36 is always rotated, the valve mechanism 39 is always operated by the centrifugal force indicated by the arrow B on the thin plate portion 40 and the pressing force of the refrigerant gas indicated by the arrow C on the surface of the bent portion 42. The resultant force in the direction of arrow A is always working as a combination of the force and the refrigerant gas pressing force. However, the spring force of the thin plate portion 40 itself that the inner side surface of the thin plate portion 40 tends to be in close contact with the side surface of the rotary valve 36 is set to be larger than the resultant force in the arrow direction A at the time of low rotation of the compressor. Yes. For this reason, when the rotational speed of the compressor becomes a high rotational speed to some extent, the centrifugal force in the direction of arrow B and the refrigerant gas pressing force in the direction of arrow C increase, and the resultant force also increases. The thin plate portion 40 gradually moves away from the side surface of the rotary valve 36 against the spring force, and the suction opening can be opened for a while. That is, as shown in FIG. 4, the lift amount of the valve mechanism 39 increases or decreases for a while from fully closed to fully open depending on the rotation speed of the compressor, and the flapper valve operating range and rotary valve operation are according to the lift amount. Zones and transition zones between them are formed.

  The flapper valve 31 described above operates when the rotation speed of the compressor is low. However, when the rotation speed is higher than a predetermined value, the flapper valve 31 is not opened or closed. The refrigerant gas suction flow rate from the first suction passage 30 decreases as the lift amount decreases.

  By using both the flapper valve 31 and the rotary valve 36 as described above, as shown in FIG. 5, when only the flapper valve is used, the compressor efficiency is increased from 500th to 1200th. However, the efficiency of the compressor gradually decreases from a high rotational speed where the rotational speed of the compressor exceeds 1200, and the rotational speed of the compressor is about 1300 when only the rotary valve is used. The compressor efficiency is relatively high from 2 to 2500, but the compressor efficiency gradually decreases from a low speed where the speed of the compressor is lower than 1300. The overall efficiency of the compressor can be improved by mechanically switching between the operation of the flapper valve 31 and the operation of the rotary valve 36 in response to the increase or decrease of the rotational speed of the compressor from the time of high or low speed to high speed. Relative It can be maintained at a high level.

  However, the structures of the rotary valve 36 and the valve mechanism 39 are not limited to those described so far, and may be structures as shown in FIGS. 6A to 6D.

  Among these, the rotary valve 36 shown in FIG. 6A has a plurality of (two in this embodiment) passages 35b of the second suction passage 35, and a plurality of (two) suction openings. ), The one opening mechanism opens and closes these suction openings. In the rotary valve 36 shown in FIG. 6B, the extending direction of the passage 35 b from the passage 35 a of the second suction passage 35 is offset with respect to the axis extending in the radial direction from the center of the rotary valve 36. Yes. In the above-described two embodiments, the structure of the valve mechanism 39 is the same as that of the above-described embodiment, so the same reference numerals are given and the description thereof is omitted.

  On the other hand, the valve mechanism 39 shown in FIG. 6C has a shape in which the lateral width is gradually reduced from the side fixed by the fixing member 41 toward the bent portion 42 with respect to the thin plate portion 40. Further, the valve mechanism 39 shown in FIG. 6D is configured such that a substantially intermediate portion between the fixing member 41 and the bent portion 42 of the thin plate portion 40 is recessed inward from both sides in the short direction, so that a part of the lateral width is obtained. It has a narrowed shape. In the above two embodiments, the structure of the rotary valve 36 is the same as that of the embodiment described with reference to FIG. 2 and FIG.

  However, the valve mechanism 39 using the thin plate portion 40 deformed with respect to the thin plate portion 40 shown in FIGS. 2 and 3 of FIGS. 6 (c) and 6 (d) has the lift amount as the vertical axis and the compressor mechanism. In the characteristic line shown when the rotational speed is on the horizontal axis, a transition region that moves from the operation region of the flapper valve 31 to the operation region of the rotary valve 36 or from the operation region of the rotary valve 36 to the operation region of the flapper valve 31, The width of the valve mechanism 39 can be made relatively narrow, and the state in which the valve mechanism 39 is not fully opened but opened halfway can be reduced.

  Further, as shown in FIG. 8, the rotary valve 36 and the valve mechanism 39 are structured such that a plurality of passages 35b (for example, four in this embodiment) are formed radially around the passage 35a and a plurality of suction openings are provided. (4) and the valve mechanism 39 may be arranged according to the number of suction openings. The valve mechanism 39 includes a thin plate portion 40, a fixing member 41 that fixes one end in the longitudinal direction of the thin plate portion 40 so as to be swingable, and a bent portion formed at an end opposite to the fixing member 41 of the thin plate portion 40. 42 is the same as that of the previous embodiment, but each thin plate portion 40 extends along the radial direction of the rotary valve 36 so that the thin plate portion 40 does not overlap with the adjacent thin plate portion 40. The shape is shifted in the same circumferential direction.

  9 to 16 show valve mechanisms 44, 52, and 55 that are structurally different from the valve mechanism 39 described so far.

  As shown in FIG. 9A, the valve mechanism 44 is a coil spring / poppet valve attached to the suction opening of the rotary valve 36, and also functions as a check valve (check valve). The structure of the valve mechanism 44 will be described with reference to FIGS. 9B and 9C. A valve seat 46 having a passage 45 communicating with the passage 35b therein, and the cylindrical body and one axial side thereof are closed. A cover 47 having a through hole 48 that is formed along the circumferential direction on the side surface of the cylindrical body, and is housed in the cover 47 and is covered with the cover 47. And a coil spring 50 disposed between the valve body 49 and the closed portion of the cover body 47. When the valve body 49 is separated from the valve seat 46, the through hole 48 and the passage 35 b of the suction passage 35 communicate with each other through the passage 45 in the valve seat 46, and the refrigerant gas flows from the suction chamber 12 into the cylinder bore working chamber 27. Sent to.

  The external input applied to the valve mechanism 44 is a biasing force that the coil spring 50 presses the valve body 49 toward the valve seat 46 for closing the suction opening of the passage 35b, and the suction opening of the passage 35b. This is a centrifugal force that presses the valve body 49 toward the closed portion of the cover 47 when the valve mechanism 44 rotates together with the rotary valve 36.

  That is, in the valve mechanism 44, when the rotary valve 36 is always rotated, a centrifugal force is exerted on the valve body 49 toward the closed portion of the cover 47, but the urging force of the coil spring 50 is used to reduce the rotation of the compressor. Sometimes it is set to be stronger than the centrifugal force. For this reason, as shown in FIG. 10, when the rotational speed of the compressor becomes a certain high rotational speed, the centrifugal force that presses the valve body 49 toward the closed portion of the cover body 47 increases, and the coil spring 50 is attached. The valve body 49 gradually moves away from the valve seat 46 against the force, and the suction opening can be opened for a while. That is, as shown in FIG. 10, the lift amount of the valve mechanism 44 increases or decreases for a while from fully closed to fully open depending on the number of rotations of the compressor, and the flapper valve operating range and the rotary valve operation according to the lift amount. Zones and transition zones between them are formed.

  A non-linear spring (not shown) may be used instead of the coil spring 50 for closing the suction opening of the passage 35b. The urging force of the non-linear spring is also set so that the centrifugal force that presses the valve body 49 toward the closed portion of the cover 47 is increased when the compressor is rotating at a low speed. By using this non-linear spring, as shown in FIG. 11, in the characteristic line shown when the lift amount of the valve mechanism 44 is the vertical axis and the rotational speed of the compressor is the horizontal axis, the operating range of the flapper valve 31 is shown. The transition region from the operation region of the rotary valve 36 to the operation region of the rotary valve 36 or from the operation region of the rotary valve 36 to the operation region of the flapper valve 31 can be made relatively narrow compared to the case of the coil spring 50. It is possible to reduce the state where the mechanism 44 is not fully opened but is opened halfway.

  However, the structures of the rotary valve 36 and the valve mechanism 44 are not limited to those described so far, and for example, structures as shown in FIGS. 12A and 12B may be used. That is, for example, a plurality of passages 35b (four in this embodiment) are formed radially around the passage 35a, a plurality of (four) suction openings are provided, and the valve mechanism 44 is also the number of the suction openings. You may make it arrange | position according to. In addition, since the structure of each valve mechanism 44 is the same as what was demonstrated until now, the same code | symbol was attached | subjected and the description was abbreviate | omitted.

  The valve mechanism 52 is a spring / magnet / poppet valve attached to the suction opening of the rotary valve 36, and also functions as a check valve (check valve). The structure of the valve mechanism 52 will be described with reference to FIGS. 13A and 13B. A valve seat 46 having a passage 45 communicating with the passage 35b therein, and a cover 47 having a through hole 48 on a side surface thereof. The valve body 49 is housed in the cover body 47 and movable along the axial direction of the cover body 47, and the coil spring 50 is disposed between the valve body 49 and the closed portion of the cover body 47. The valve mechanism 44 is the same as the valve mechanism 44 except that a magnet 53 is provided on the closing portion side of the cover 47 and the valve body 49 is formed of a material that can be adsorbed to a magnet such as iron. Have On the other hand, when the valve body 49 is separated from the valve seat 46, the through hole 48 and the passage 35 b of the suction passage 35 communicate with each other via the passage 45 in the valve seat 46, and the refrigerant gas flows from the suction chamber 12 into the cylinder bore working chamber 27. The action of being sent to is common.

  The external input applied to the valve mechanism 52 is a biasing force by which the coil spring 50 presses the valve body 49 toward the valve seat 46 for closing the suction opening of the passage 35b, and the suction opening of the passage 35b. For opening the rotary valve 36, the centrifugal force that presses the valve body 49 toward the closed portion of the cover 47 when the rotary valve 36 rotates and the magnetic force of the magnet 53 within a certain distance from the magnet 53.

  That is, in this valve mechanism 52, when the rotary valve 36 is always rotated, a centrifugal force is exerted on the valve body 49 toward the closed portion of the cover 47, but at a low speed of the compressor, the centrifugal force is greater than the centrifugal force. The biasing force of the coil spring 50 is set to be strong.

  For this reason, as shown in FIG. 13, when the rotational speed of the compressor becomes a high rotational speed to some extent, the centrifugal force that presses the valve body 49 toward the closed portion of the cover body 47 increases, and the coil spring 50 is attached. The valve element 49 gradually moves away from the valve seat 46 against the force. Accordingly, the valve body 49 gradually approaches the magnet 53, and the magnetic force of the magnet 53 reaches the valve body 49 from a certain distance.

  That is, as shown in FIG. 14, the lift amount of the valve mechanism 52 varies from fully closed to fully open depending on the rotation speed of the compressor, and according to the lift amount, the flapper valve operating range, the rotary valve operating range, A transition zone between them is formed. In addition, when the valve mechanism 52 is opened, the magnetic force of the magnet 53 is added as an external input to the urging force of the coil spring 50, so that as shown by the solid line in FIG. In the characteristic line shown when the lift amount of the valve mechanism 52 is the vertical axis and the rotational speed of the compressor is the horizontal axis, the operating range of the flapper valve 31 is shifted to the operating range of the rotary valve 36 or the rotary valve 36 is operated. The transition region that moves from the region to the operation region of the flapper valve 31 can be made relatively narrow compared to the case of the valve mechanism 44, and the state in which the valve mechanism 52 is not fully opened but is opened halfway. It can be reduced. On the other hand, when the valve mechanism 52 is closed, the magnetic force of the magnet 53 acts as a drag against the action of the valve body 49 approaching the valve seat 46 side, so that the transition region is opened as shown by the broken line in FIG. It shifts when the rotation speed of the compressor is low compared to the valve time.

  In this valve mechanism 52, a non-linear spring may be used instead of the coil spring 50. By using a non-linear spring, the transition range from the operation region of the flapper valve 31 to the operation region of the rotary valve 36 or from the operation region of the rotary valve 36 to the operation region of the flapper valve 31 is relatively narrow. It is possible to reduce the state in which the valve mechanism 52 is not fully opened but is opened halfway.

  The valve mechanism 55 is an electromagnetic valve attached to the suction opening of the rotary valve 36 and also functions as a check valve (check valve). In the embodiment shown in FIG. 15, the valve mechanism 55 is configured such that the passage 35 b is eliminated from the suction passage 35 of the rotary valve 36 and the passage 35 a is provided with a suction opening extending in the axial direction of the drive shaft 14. The rotary valve 36 is attached to a suction opening provided at the axial end.

  The structure of the valve mechanism 55 will be described with reference to FIG. 15. The valve mechanism 55 includes a valve seat 46 having a passage 45 communicating with the passage 35b, a cylindrical body, and a closing portion for closing one side in the axial direction. In addition, a cover 47 having a through-hole 48 provided side by side along the circumferential direction on the side surface of the cylindrical body, and accommodated in the cover 47 and movable along the axial direction of the cover 47 The valve body 49, the coil spring 50 disposed between the valve body 49 and the closed portion of the cover body 47, and the electromagnetic coil 57 disposed on the radially outer side of the valve body 49.

  The electromagnetic coil 57 is formed by winding an electric wire, and an intermittent voltage is applied via an electric circuit (not shown). When the valve body 49 is separated from the valve seat 46, the through hole 48 and the passage 35 b of the suction passage 35 communicate with each other through the passage 45 in the valve seat 46, and the refrigerant gas flows from the suction chamber 12 into the cylinder bore working chamber 27. Sent to.

  The external input applied to the valve mechanism 55 is a biasing force by which the coil spring 50 presses the valve body 49 toward the valve seat 46 for closing the suction opening of the suction passage 35. For opening the opening, an electromagnetic force is applied to the valve body 49 so as to resist the urging force of the coil spring 50 by applying a current to the electromagnetic coil 57.

  That is, the valve mechanism 55 does not use the centrifugal force generated by the rotation of the rotary valve 36, and the switching between the operation area of the flapper valve 31 and the rotary valve 36 is compressed by a rotation speed detection device (not shown) or the like. If the rotation speed of the machine is detected and, as a result, it is determined that the rotation speed is low, the current application to the electromagnetic coil 57 is turned off, and if the rotation speed is determined to be high, the current application to the electromagnetic coil 57 is turned on. Done. For this reason, the lift amount of the valve mechanism 55 is not affected by the rotational speed of the compressor, and can be switched instantaneously as shown in FIG. 16, and the operating range of the flapper valve 31 and the operating range of the rotary valve 36 There can be no transition zone.

  Even when the valve mechanisms 44, 52, and 55 as described above are adopted, by using the flapper valve 31 and the rotary valve 36 in combination, the rotation of the compressor can be performed from a low speed to a high speed or from a high speed to a low speed. The overall efficiency of the compressor is kept relatively high by switching the operation of the flapper valve 31 and the operation of the rotary valve 36 to the more efficient one of the compressor in response to the change in the number. Can do. By attaching the valve mechanism 52 to the suction opening of the rotary valve 36, it is possible to relatively clarify the operation switching of the valve mechanism 52. Further, by attaching the valve mechanism 55 to the suction opening of the rotary valve 36, it is possible to relatively clarify the operation switching of the valve mechanism 55 and to arbitrarily control the rotation speed of the compressor at the time of switching. It becomes.

  The piston-type swash plate type compressor 1 to which the present invention is used is not limited to the electric type shown in FIG. 1, and may be a belt-driven type as shown in FIG. The belt-driven compressor 1 will be described below with reference to FIG.

  This compressor 1 is also used in a vehicle air conditioner and constitutes a part of a known refrigeration cycle. That is, the compressor 1 compresses the refrigerant gas that has been reduced in temperature and pressure by an evaporator (not shown) to increase the temperature and pressure, and sends the compressed refrigerant gas to a condenser (not shown).

  The configuration of the compressor 1 will be described. A cylinder block 2, a front side member 3 fixed to the front side of the cylinder block 2, a rear side member 4 fixed to the rear side of the cylinder block 2, and a drive shaft. 14, and the cylinder block 2, the front side member 3, and the rear side member 4 constitute a substantially cylindrical casing 1 a by inserting and fastening the fastening bolts 10 along the cylinder bore axial direction. is doing.

  The crank chamber 9 is defined by joining the front side member 3 and the cylinder block 2, and the suction chamber 12 is connected to the rear side member 4 by joining the cylinder block 2 and the rear side member 4 via the plate 11. And a discharge chamber 13 are defined.

  The suction chamber 12 is for accommodating the refrigerant gas supplied to the cylinder bore working chamber 27, and is formed in the central portion of the rear side member 4, and has a predetermined flow rate at a suction port 32 leading to an outlet side of an evaporator (not shown). It communicates via a path and can communicate with the cylinder bore working chamber 27. The discharge chamber 13 is for containing the refrigerant gas discharged from the cylinder bore working chamber 27, and is continuously formed around the suction chamber 12, and has a discharge port 33 leading to the inlet side of a condenser (not shown). The cylinder bore working chamber 27 can communicate with the cylinder bore.

  The drive shaft 14 is mainly accommodated in the crank chamber 9, and one end thereof protrudes from the front side member 3, and this protruding portion is connected to a traveling engine (not shown) via a belt and a pulley. The power of is transmitted to rotate. Further, the opposite end of the drive shaft 14 passes through the cylinder block 2 and reaches the suction chamber 12 of the rear side member 4. The drive shaft 14 is rotatably held by the front side member 3 and the cylinder block 2 via a bearing or the like.

  The cylinder block 2 is formed with a plurality of cylinder bores 21 arranged at equal intervals on a circumference around the drive shaft 14 so as to surround the drive shaft 14. In each cylinder bore 21, a single-head piston 22 composed of a hollow head portion 22a and a tail portion 22b is inserted so as to be reciprocally slidable. A shoe receiving portion having a concave curved surface is formed opposite to the head portion 22a and the tail portion 22b of the one-head piston 22 in order to dispose the shoe 23.

  Furthermore, a thrust flange 24 that rotates integrally with the drive shaft 14 is fixed in the crank chamber 9 that communicates with the cylinder bore 21 of the cylinder block 2. The thrust flange 24 is rotatably supported via the bearing mechanism 25 with respect to the front side member 3. A swash plate 26 is connected to the thrust flange 24 via a link mechanism 17, and this swash plate 26 is attached so as to be tiltable around a hinge ball 28 provided on the drive shaft 14. The thrust flange 24 rotates integrally with the rotation of the thrust flange 24. And the swash plate 26 is moored by the tail part 22b of the one-headed piston 22 via a pair of shoes 23 provided so that the peripheral part might be pinched | interposed back and forth.

  Accordingly, in the belt-driven compressor 1, the swash plate 26 also rotates with the rotation of the drive shaft 14 due to the above configuration, and the rotational movement of the swash plate 26 is caused by the rotation of the one-head piston 22 via the shoe 23. The volume is converted into a reciprocating linear motion, and the volume of the cylinder bore working chamber 27 formed between the single-headed piston 22 and the plate 11 in the cylinder bore 21 is changed by the reciprocating motion of the single-headed piston 22.

  By the way, the belt-driven compressor 1 includes the following two intake valve mechanisms as a mechanism for supplying refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27. Among these, the first suction valve mechanism for supplying the refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27 corresponds to each cylinder bore 21 around the through hole 29 through which the drive shaft 14 of the plate 11 is inserted. A first suction passage 30 is formed, and the first suction passage 30 is opened and closed by a flapper valve 31 provided as a suction valve on the front side end surface of the plate 11. The flapper valve 31 is also a reed valve in this embodiment.

  The second suction valve mechanism for supplying the refrigerant gas from the suction chamber 12 into the cylinder bore working chamber 27 has one end communicating with the suction chamber 12 and the other end of the drive shaft 14 on the rear side member 4 side. Is provided with a substantially U-shaped second suction passage 35 (35a, 35b, 35c) that intermittently communicates with the inside of the cylinder bore working chamber 27, thereby being configured as a rotary valve 36 and rotating integrally with the drive shaft 14. As a result, the passage 35d formed in the cylinder block 2 is intermittently communicated. Since the detailed configuration of the second intake valve mechanism is the same as that of the previous embodiment, the same reference numerals are given and description thereof is omitted.

  On the other hand, the mechanism for discharging the refrigerant gas from the cylinder bore working chamber 27 to the discharge chamber 13 forms a discharge passage 37 corresponding to the cylinder bore 21 in the plate 11, and this discharge passage 37 is provided on the rear side end face of the plate 11. The discharge valve 38 is opened and closed.

  However, also in this belt drive type compressor 1, the valve mechanism 39 shown in FIGS. 2, 6, and 8 and the valve mechanism 44 shown in FIGS. 9 and 10 (a nonlinear spring is used instead of the coil spring 50). 13), the valve mechanism 52 shown in FIG. 13 can be attached to the suction opening that opens to the side of the rotary valve. Although not shown, the passage 35b is eliminated from the suction passage 35 and the passage 35a is provided with a suction opening extending in the axial direction of the drive shaft 14, whereby the valve mechanism 55 shown in FIG. It is possible to attach to the inhalation opening part opened to the axial direction end.

  Therefore, by using the flapper valve 31 and the rotary valve 36 having the valve mechanism 39, 44, 52, or 55 in combination, as shown in FIG. The compressor efficiency is relatively high from 2000th to 3500th, but the efficiency of the compressor gradually decreases from a high speed exceeding 3500th, and only the rotary valve is used. The compressor efficiency is relatively high when the compressor speed is from 5500 to 7500, but the compressor efficiency is gradually increased from such a low speed that the compressor speed falls below 5500. However, the operation of the flapper valve 31 and the operation of the rotary valve 36 are mechanically corresponding to the increase / decrease of the rotation speed of the compressor from the low rotation to the high rotation or from the high rotation to the low rotation. Cut into It is possible to maintain the overall efficiency of the compressor to a relatively high state by replacing.

FIG. 1 is a cross-sectional view showing the overall structure of an electric compressor as an example of a compressor in which the present invention is used. FIG. 2 is an explanatory view showing the configuration of a leaf spring / reed valve mainly composed of a leaf spring-like member as a valve mechanism for opening and closing the suction opening of the rotary valve. FIG. 2 (a) is a leaf spring / lead. The closed state of the valve is shown, and FIG. 2B shows the open state of the leaf spring / reed valve. FIG. 3 is an enlarged explanatory view of a leaf spring / reed valve showing a mechanism in which the leaf spring / reed valve operates toward opening. FIG. 4 is a characteristic diagram showing the relationship between the rotational speed of the compressor and the efficiency of the compressor when the present invention is adopted in the electric compressor. FIG. 5 is a characteristic diagram showing the opening of the leaf spring / reed valve in relation to the rotational speed of the compressor. 6 (a) to 6 (d) are explanatory views showing modifications of the leaf spring / reed valve shown in FIG. 7 is a characteristic diagram showing the opening degree of the leaf spring / reed valve in relation to the rotational speed of the compressor when the shape of the leaf spring-like member of the leaf spring / reed valve shown in FIG. 6 is varied. . FIG. 8 is an explanatory view showing a further modification using a plurality of leaf springs / reed valves shown in FIG. FIG. 9 is an explanatory view showing the configuration of a coil spring / poppet valve mainly composed of a coil spring as a valve mechanism for opening and closing the suction opening of the rotary valve. FIG. 9 (a) shows the state of attachment of the coil spring / poppet valve. FIG. 9B shows a closed state of the coil spring / poppet valve, and FIG. 9C shows an open state of the coil spring / poppet valve. FIG. 10 is a characteristic diagram showing the opening degree of the coil spring / poppet valve in relation to the rotational speed of the compressor. FIG. 11 is a characteristic diagram showing the opening degree of the nonlinear spring / poppet valve in relation to the rotational speed of the compressor when a nonlinear spring is used instead of the coil spring. FIG. 12 is an explanatory view showing a modification using a plurality of coil spring / poppet valves shown in FIG. 10 or a plurality of nonlinear spring / poppet valves shown in FIG. FIG. 13 is an explanatory view showing a configuration of a spring, magnet, poppet valve in which a magnet is added to a coil spring / poppet valve or a non-linear spring / poppet valve, and FIG. 13 (a) is a closed state of the spring, magnet, poppet valve. FIG. 13B shows an open state of the spring, magnet, and poppet valve. FIG. 14 is a characteristic diagram showing the opening of the spring, magnet, poppet valve in relation to the rotational speed of the compressor. FIG. 15 is an explanatory view showing a configuration using a solenoid valve as a valve mechanism for opening and closing the suction opening of the rotary valve. FIG. 15A shows a closed state of the solenoid valve, and FIG. The open state of the solenoid valve is shown. FIG. 16 is a characteristic diagram showing that the solenoid valve is opened regardless of the rotational speed of the compressor. FIG. 17 is a cross-sectional view showing the overall structure of a belt-driven compressor as an example of a compressor in which the present invention is used. FIG. 18 is a characteristic diagram showing the relationship between the rotational speed of the compressor and the efficiency of the compressor when the present invention is adopted in the belt-driven compressor.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Compressor 1a Casing 4 Rear side member 9 Crank chamber 12 Suction chamber 14 Drive shaft 20 Electric motor 22 Piston 26 Swash plate 27 Cylinder bore working chamber 30 First suction passage 31 Flapper valve 35 Second suction passage 35ab thru 35b passage 36 Rotary Valve 39 Valve mechanism (leaf spring / reed valve)
40 Thin plate part 42 Bent part 44 Valve mechanism (coil spring / poppet valve)
45 passage 46 valve seat 47 cover body 48 through hole 49 valve body 50 coil spring (elastic member)
52 Valve mechanism (spring, magnet, poppet valve)
53 Magnet 55 Valve mechanism (solenoid valve)
57 Electromagnetic coil

Claims (5)

A drive shaft that passes through the crank chamber and is rotatably supported by the casing, a swash plate that is disposed in the crank chamber and rotates in synchronization with the rotation of the drive shaft, and the inside of the cylinder bore as the swash plate rotates. In a swash plate type piston compressor comprising at least a reciprocating piston and a suction pressure space defined in a rear side member constituting the casing,
A first suction passage that directly communicates the suction pressure space and the cylinder bore working chamber is provided, a flapper valve that opens and closes the first suction passage is disposed, and a rear side member side end portion of the drive shaft is disposed. The rotary valve is configured by providing a second suction passage having one end communicating with the suction pressure space and the other end intermittently communicating with the cylinder bore working chamber, and the second suction configuring the rotary valve. A refrigerant gas supply mechanism from a suction pressure space of a compressor, wherein a suction opening on one end side of the passage is provided with a valve mechanism for opening and closing the suction opening. The valve mechanism includes a thin plate portion that is swingably provided in the vicinity of the suction opening formed on the side surface of the rotary valve, and the spring force of the thin plate portion is used when the compressor rotates at a low speed. The suction opening is closed, and the suction opening of the rotary valve is separated from the suction opening of the rotary valve against the spring force of the thin plate portion using centrifugal force when the compressor rotates at a high speed. The refrigerant gas supply mechanism from the suction pressure space of the compressor according to claim 1, wherein The valve mechanism includes a valve seat having a passage communicating with a passage having a suction opening portion of the second suction passage, and one of the axial directions is closed by the closing portion and is joined to the valve seat on the other opening side. A cover body, a through-hole opened in a side surface of the cover body, a valve body movable along the axial direction of the cover body, and an elastic member disposed on the closing portion side with respect to the valve body At least configured, the through-hole of the cover body can communicate with the suction opening of the rotary valve, and the urging force of the elastic member against the valve body is larger than the centrifugal force when the compressor rotates at a low speed, and is compressed The refrigerant gas supply mechanism from the suction pressure space of the compressor according to claim 1, wherein the refrigerant gas is set to be smaller than the centrifugal force at the time of high rotation of the compressor. 4. The compressor according to claim 3, wherein the valve mechanism includes a magnet disposed on a closing portion side of the cover, and the valve body is formed of a material that can be adsorbed to the magnet. A refrigerant gas supply mechanism from the suction pressure space. The valve mechanism includes a valve seat having a passage communicating with a passage having a suction opening portion of the second suction passage, and one of the axial directions is closed by the closing portion and is joined to the valve seat on the other opening side. A cover body, a through-hole opened in a side surface of the cover body, a valve body movable along the axial direction of the cover body, and an elastic member disposed on the closing portion side with respect to the valve body, An electromagnetic coil to which a voltage is applied is formed by winding an electric wire on the radially outer side of the valve body, and the through hole of the cover body can communicate with the suction opening of the rotary valve. The valve body closes the through hole by the urging force of the elastic member against the valve body, and the valve body resists the urging force of the elastic member by applying a voltage to the electromagnetic coil. And is drawn to the closed side of the cylindrical body to open the through hole. Coolant gas supply mechanism from the suction pressure space of the compressor according to claim 1,.

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