Variable displacement compressor with adjustable swashplate inclination

Abstract

Variable displacement compressor (100) comprising a housing accommodating an outlet chamber (142); a suction chamber (141); a crankcase (140) and a cylinder bore (101a), a piston (136) provided in the cylinder bore (101a), a drive shaft (110) rotatably supported by the housing, a rotor (112) rotating integrally with the drive shaft (110), a swashplate (111) rotating synchronously with the rotation of the rotor (112), the two components being connected by a linkage, a converter mechanism converting a rotation of the swashplate (111) into a reciprocating motion of the piston (136), and a pressure control valve (300) capable of controlling the internal pressure of the crankcase (140) according to a valve opening, wherein when the valve opening is changed to alter the internal pressure of the crankcase (140), an exhaust capacity for compressing and expelling coolant drawn from the suction chamber (141) into the cylinder bore (101a) is changed by altering the stroke of the piston (136) by changing the inclination of the swashplate (111) to the drive shaft (110) while the swashplate (111) slides on the drive shaft (110), wherein an inclination angle of the swashplate (111) defines the height of the stroke of the piston (136) and thus the displacement power, characterized by the fact that, when no compression load is applied to the swashplate (111), the swashplate (111) is connected such that it is inclined relative to the rotor (112) such that a compression process area on one side of a positive direction of rotation of the swashplate (111) is further away from a support side of an axial bearing formed on the rotor (112) than a suction process area on one side of a negative direction of rotation of the swashplate (111) when viewed from a position corresponding to a top dead center of the piston (136), and when a compression load is applied to the swashplate (111), the inclination of the swashplate (111) is suppressed, wherein a plane (P1) containing the axis of the drive shaft (110) and a top dead center and a bottom dead center of the swashplate (111) divides the swashplate (111) into a compression process side and a suction process side, wherein a plane (P3) contains a line of intersection (G) between the plane (P1) and a ring-like plane (P2) of the swashplate (111) and is orthogonal to the plane (P1), wherein the ring-shaped plane (P2) of the swashplate (111) tilts by an angle (β) from the plane (P3) as it moves in a direction in which the outermost part on the compression process side is furthest away from a reference level (R) of the rotor (112), while the outermost part on the suction process side is closest to the reference level (R) of the rotor (112), where the angle between plane (P2) and plane (P3) is zero degrees when the swashplate tilt angle is zero degrees and there is no compression load, and where the angle between the plane (P2) and the plane (P3) is also zero degrees when the swashplate tilt angle is at its maximum and a compaction load is present.

Description

TECHNICAL AREA OF INVENTION

[0001] The present invention relates to a compressor with variable displacement and variable swashplate inclinations, which is used in particular in an air conditioning system for vehicles. STATE OF THE ART

[0002] Patent document 1 discloses a joint mechanism (coupling mechanism) that rotatably connects two component parts by means of a connecting pin. Patent document 2 discloses a technique for providing a device for regulating relative movement in order to stabilize the swashplate's wobble behavior with respect to the drive shaft. PRINTED FORMS OF THE STATE OF TECHNICAL PATENT PRINTED FORMS Patent Publication 1: JP 2003 172333 A Patent Publication 2: JP 2002 364530 A SUMMARY OF THE INVENTION PROBLEMS TO BE SOLVED BY THE INVENTION

[0003] In the joint mechanism (coupling mechanism) disclosed in patent document 1, the through-hole of the swashplate is inclined, causing wear on a contact area between the edge of the through-hole and the circumferential surface of the drive shaft. This prevents the swashplate from tilting smoothly if it is tilted from a vertical direction by an axial load derived from the compression load. Such wear can progress particularly on the side of the maximum swashplate inclination, as the compression load is greater there, thus blocking the swashplate's tilting movement. Other variable displacement compressors are known from DE 60 2004 005 943 T2; DE 198 08 323 A1; and EP 1 850 003 A2.US 2007 / 0220859 A1 states that when a compression load is applied to the swashplate, the tilt of the swashplate is suppressed as long as the swashplate tilt angle is minimal.

[0004] It would therefore be helpful to provide a variable displacement compressor in which the wear of a contact part between the through-hole of the swashplate and the circumferential surface of the drive surface is prevented and the tilting movement of the swashplate is carried out gently. MEANS TO SOLVE THE PROBLEMS

[0005] To solve the problem described above, the present invention is a variable displacement compressor comprising a housing that accommodates an outlet chamber; a suction chamber; a crank chamber and a cylinder bore, a piston provided in the cylinder bore, a drive shaft rotatably supported by the housing, a rotor that rotates integrally with the drive shaft, a swashplate that rotates synchronously with a rotation of the rotor, which are connected by a connecting device, a converter mechanism that converts a rotation of the swashplate into a reciprocating motion of the piston, and a pressure control valve that can control an internal pressure of the crank chamber according to a valve opening, wherein when the valve opening is changed to alter the internal pressure of the crankcase, an exhaust capacity for compressing and expelling coolant drawn from the intake chamber into the cylinder bore is changed by altering the stroke of the piston by changing the inclination of the swashplate to the drive shaft while the swashplate slides on the drive shaft, where the tilt angle of the swashplate defines the height of the piston stroke and thus the displacement power, characterized by the fact that, If no compression load is applied to the swashplate, and the swashplate is connected in such a way that it is inclined relative to the rotor, a compression process area on one side of a positive direction of rotation of the swashplate is further away from a support side of an axial bearing formed on the rotor than a suction process area on one side of a negative direction of rotation of the swashplate when viewed from a position corresponding to a top dead center of the piston, and when a compression load is applied to the swashplate, the tilt of the swashplate is suppressed, wherein a plane P1, which contains the axis of the drive shaft and a top dead center and a bottom dead center of the swashplate, divides the swashplate into a compression process side and a suction process side, wherein a plane P3 contains a line of intersection between the plane P1 and a ring-like plane P2 of the swashplate and is orthogonal to the plane P1, wherein the ring-shaped plane P2 of the swashplate tilts by an angle β from the plane P3 as it moves in a direction in which the outermost part on the compression process side is furthest away from a reference level of the rotor, while the outermost part on the suction process side is closest to the reference level of the rotor, where the angle between plane P2 and plane P3 is zero degrees when the swashplate tilt angle is zero degrees and there is no compression load, and where the angle between plane P2 and plane P3 is also zero degrees when the swashplate tilt angle is at its maximum and a compaction load is present.

[0006] When such a variable displacement compressor is operated to apply a compression load to the swashplate, the side of the through-hole is in contact with the circumferential surface of the drive shaft in a manner similar to a line contact, so that wear of a contact part between the through-hole of the swashplate and the circumferential surface of the drive shaft is prevented and the tilting movement of the swashplate is carried out gently.

[0007] It is preferable that the ratio of the distance of the swashplate's compression process area from the axial bearing's support side to the distance of the suction process area from the support side, viewed from the position corresponding to top dead center, is maximized when the inclination is at its maximum. In such a configuration, the compression load decreases as the inclination decreases from its maximum inclination, so that the through-hole side is in contact with the drive shaft's circumferential surface in a manner similar to line contact, regardless of the swashplate inclination of the variable displacement compressor during operation.

[0008] It is preferable that the minimum tilt angle of the swashplate be set to approximately 0° and that the ratio of the distance of the swashplate's compression process area from the support side of the thrust bearing to another distance of the suction process area from the support side, viewed from the position corresponding to top dead center, is minimal when the tilt is minimal. If the minimum tilt angle is approximately 0°, the effect of the compression load is too small to tilt the swashplate unnecessarily. EFFECT ACCORDING TO THE INVENTION

[0009] The present invention can provide a variable displacement compressor that effects a gentle tilting movement with a simple structure. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 shows a longitudinal sectional view of a variable displacement compressor according to an embodiment of the present invention. Fig. Figure 2 shows the coupling arm of the Fig. 1, wherein (a) shows a top view and (b) shows a view of an arrow in a direction A shown in (a). Fig. Figure 3 shows a view of an arrow, and it shows a connected body of the drive shaft and the rotor in the Fig. 1. Fig. Figure 4 shows a view of an arrow, and it shows the swashplate of the Fig. 1. Fig. Figure 5 shows a front view of a connected body of the drive shaft, rotor, coupling arm and swashplate of the Fig. 1. Fig. Figure 6 shows a top view of the swashplate as seen from the side of the rotor. Fig. 1. Fig. Figure 7 shows a partial top view of a connected body of the second connecting pin and the swashplate of the Fig. 6. Fig. Figure 8 shows the positional relationship between the rotor, the drive shaft, the coupling arm and the swashplate, wherein (a) shows a top view of the connected body of the drive shaft and the rotor, (b) shows a front view of the coupling arm, and (c) shows a top view of the swashplate. Fig. Figure 9 describes an inclination angle of the swashplate of the Fig. 1, where (a) shows a state of maximum tilt, and (b) shows another state of minimum tilt. In (a) and (b), a view of an arrow of a second connecting pin when viewed along a direction C2 or C1 is in each case top left, a view of an arrow of the swashplate when viewed along a direction B2 or B1 is in each case top right, and a side view of a connected body is at the bottom. Fig. Figure 10 shows a schematic side view of the swashplate to describe an inclination when the variable displacement compressor is operating. Fig. 1 is operated. Fig. Figure 11 shows a partial, enlarged, schematic sectional view of an enlarged contact part between the swashplate and the drive shaft of the Fig. 8. ) Fig. Figure 12 shows a top view of a swashplate when viewed from one side of the rotor of a variable displacement compressor according to another embodiment of the present invention. Examples of how to implement the invention

[0010] A variable displacement compressor according to the present invention can be visually described as follows with reference to virtual planes (planes P1-P3). The present invention is a variable displacement compressor comprising a housing having compartments of an outlet chamber, a suction chamber, a crank chamber, and a cylinder bore; a piston provided in the cylinder bore; a drive shaft rotatably supported by the housing; a rotor attached to the drive shaft in such a way that it rotates integrally with the drive shaft; a swashplate attached to the drive shaft in a sliding contact through a through-hole into which the drive shaft is inserted, rotating synchronously with the rotor; components connected by a linkage device to change the inclination from an axis of the drive shaft; and a converter mechanism.which converts a rotation of the swashplate into a reciprocating motion of the piston, and a pressure control valve that can control an internal pressure of the crankcase, wherein an opening of the control valve is set to change the internal pressure of the crankcase, wherein a stroke of the piston is set by changing the inclination of the swashplate, and wherein a coolant that is drawn from the suction chamber into the cylinder bore is compressed and discharged to the exhaust chamber, characterized in that, a plane P2, defined as an annular plane of the swashplate, is inclined at a predetermined angle with respect to a plane P3 such that a connected body of the drive shaft, the rotor, the connecting device and the swashplate has an outermost part of the plane P2 in a compression process region which is further away from a support side of an axial bearing formed on the rotor than another outermost part which is symmetrical to the plane P2 in a suction process region, wherein The swashplate is divided into the compression process area and the suction process area by a plane P1 which contains an axis and a top dead center of the swashplate, while the plane P3 is orthogonal to the plane P1 and contains a line of intersection between the plane P1 and the plane P2.

[0011] When such a variable displacement compressor is operated to apply a compression load to the swashplate, the side of the through-hole is in contact with the circumferential surface of the drive shaft in a manner similar to a line contact, so that wear of a contact part between the through-hole of the swashplate and the circumferential surface of the drive surface is prevented and the tilting movement of the swashplate is carried out gently.

[0012] It is preferable that the predetermined angle 5 decreases when the swashplate inclination decreases from a maximum inclination according to a maximum value of the predetermined angle. In such a configuration, the compression load decreases when the inclination decreases from the maximum inclination according to the maximum compression load, so that the side of the through-hole is in contact with the circumferential surface of the drive shaft in a manner similar to line contact, regardless of the swashplate inclination of the variable displacement compressor during operation.

[0013] It is preferable that the minimum tilt angle of the swashplate be set to approximately 0°, and that the predetermined angle corresponding to the minimum tilt angle is also approximately 0°. If the minimum tilt angle is approximately 0°, the compression load is too weak to tilt the swashplate unnecessarily.

[0014] Desirable examples of the variable displacement compressor are described below with reference to the drawings. (1) Variable displacement compressor

[0015] In the Fig. 1 has a variable displacement compressor 100 as a clutchless compressor, a cylinder block 101 with cylinder bores 101a, a front housing 102 provided at one end of the cylinder block 101, and at the other end of the cylinder block 101 a cylinder head 104, which is provided with a valve plate 103.

[0016] A swashplate 111 is provided around the center of the drive shaft 110, which passes through the crankcase 140, which is sectioned by the cylinder block 101 and the front housing 102. The swashplate 111 is provided with a through-hole 111a into which the drive shaft 110 is inserted, and the through-hole 111a is designed such that the swashplate 111 can be tilted between a maximum tilt angle and a minimum tilt angle with an axis K that is orthogonal to a plane containing the top dead center of the swashplate and the axis of the drive shaft, and which is orthogonal to the annular plane of the swashplate 111. The swashplate 111 is connected to a rotor 112, which is attached to the drive shaft 110, by a coupling mechanism 120, and the side surface of the through-hole 111a is slidably supported by the circumferential surface of the drive shaft 110 so that the tilt angle θ is variable.

[0017] The through-hole 111a is provided with a part for regulating a minimum inclination, which is to be brought into contact with the drive shaft 110. In this example, the part for regulating the minimum inclination of the through-hole 111a is configured to have a swashplate inclination angle θ of approximately 0°, assuming that the annular plane of the swashplate 111, orthogonal to the drive shaft 110, also has a swashplate inclination angle of 0°. The minimum inclination angle of approximately 0° means that the minimum inclination angle is greater than -0.5° and less than 0.5°. It is preferable that the minimum inclination angle be set between 0° and less than 0.5°.

[0018] A tilt reduction spring 114, a compression helical spring that preloads the swashplate 111 downwards to the minimum tilt angle, is provided between the rotor 112 and the swashplate 111, while a tilt increase spring 115, a compression helical spring that preloads the swashplate 111 upwards to a predetermined tilt angle smaller than the maximum tilt angle, is provided between the swashplate 111 and a spring support element 116. Since the preload force of the tilt increase spring 115 is designed to be greater than the preload force of the tilt reduction spring 114, the swashplate 111 is positioned at a predetermined tilt angle such that the resultant force of the preload force of the tilt reduction spring 114 and the preload force of the tilt increase spring 115 is zero when the drive shaft is not rotating.

[0019] One end of the drive shaft 110 penetrates a hub section 102a, which projects from the front housing 102, so that it extends outwards to connect to a power transmission device (not shown). A shaft seal 130 is arranged between the drive shaft 110 and the hub section 102a to seal the interior from the exterior. The drive shaft 110 and the rotor 112 are supported radially by bearings 131 and 132, and axially by bearings 133 and an axial plate 134. Power is transmitted from an external drive source to the power transmission device to rotate the drive shaft 110 synchronously with the rotation of the power transmission device. The gap between the axial plate 134 and the drive shaft 110 is adjusted to a predetermined distance for contact with the axial plate 134 by an adjusting screw 135.

[0020] The piston 136 is positioned in the cylinder bore 101a, and the outer circumference of the swashplate 111 is located within an interior space formed by one end of the piston 136, which projects towards the crankcase 140. The swashplate 111 is designed to interact with the piston 136 via a pair of sliding blocks 137. Thus, the piston 136 can move back and forth within the cylinder bore 101a as the swashplate 111 rotates.

[0021] The cylinder head 104 is sectioned into a suction chamber 141 at its center and an exhaust chamber 142, which surrounds a radially outer part of the suction chamber 141 in an annular fashion. The suction chamber 141 is connected to the cylinder bore 101a by a connecting hole 103a and a suction valve (not shown), which are formed in the valve plate 103. The exhaust chamber 142 is connected to the cylinder bore 101a by an exhaust valve (not shown) and a connecting hole 103b, which is formed in the valve plate 103.

[0022] The front housing 102, the cylinder block 101, the valve plate 103 and the cylinder head 104 are fastened via a gasket (not shown) with through bolts 105 to form a compressor housing.

[0023] In the Fig. A silencer is provided on the upper side of the cylinder block 101. The silencer has a cover element 106 and a forming wall 101b, which is formed on the upper side of the cylinder block 101, and they are fastened by a screw with a sealing element (not shown). A check valve 200 is provided in the silencer chamber 143. The check valve 200 is provided at a connecting part between the connecting path 144 and the silencer chamber 143 and operates in response to the pressure difference between the connecting path 144 (upstream) and the silencer chamber 143 (downstream). For example, the connecting path 144 is closed when the pressure difference is less than a predetermined value, and the connecting path 144 is opened when the pressure difference is greater than the predetermined value.Thus, the outlet chamber 142 is connected to a coolant cycle on the outlet side of an air conditioning system by an outlet path which includes the connection path 144, the check valve 200, the silencer chamber 143 and an outlet port 106a.

[0024] The cylinder head 104 is provided with a suction port 104a and a connecting path 104b. The suction chamber 141 is connected to a coolant cycle on the suction side of the air conditioning system by a suction path that includes the connecting path 104b and the suction port 104a. The suction path extends in a straight line across a portion of the exhaust chamber 142 from the radially outer part of the cylinder head 104.

[0025] The cylinder head 104 is further equipped with a control valve 300. The control valve 300 controls an opening of the connecting path 145, which connects the exhaust chamber 142 to the crankcase 140, thus controlling the amount of exhaust gas introduced into the crankcase 140. The coolant in the crankcase 140 flows to the intake chamber 141 through the connecting path 101c, the chamber 146, and an opening 103c formed in the valve plate 103.

[0026] Therefore, the outlet capacity of the variable displacement compressor 100 can be variably controlled by changing the pressure in the crankcase 140 by the control valve 300 in order to change the inclination of the swashplate 111 (namely to change the stroke of the piston 136).

[0027] When the air conditioning system is operating (i.e., when the variable displacement compressor 100 is running), an electric current fed into a solenoid embedded in the control valve 300 is adjusted based on an external signal to control the outlet capacity so that the pressure in the suction chamber 141 is set to a predetermined value. The control valve 300 can control the suction pressure as desired, depending on the external environment.

[0028] When the air conditioning system is not in operation (i.e., when the variable displacement compressor 100 is at rest), the electrical current supplied to the solenoid embedded in the control valve 300 is switched off to forcibly open the connecting path 145 in order to control the outlet capacity of the variable displacement compressor to a minimum. (2) Coupling mechanism

[0029] The drive shaft 110 is attached to the rotor 112, and a pair of first arms 112a are provided such that they project from the rotor 112. An end 121a of a coupling arm 121, which has an approximately cylindrical shape, is guided in the pair of first arms 112a. A first connecting pin 122, as a connecting device, is inserted in a through-hole 112b formed in the first arm 112a and also in a through-hole 121b formed in the end 121a of the coupling arm 121, so that the coupling arm 121 can rotate about a shaft center of the first connecting pin 122 by being guided through the pair of first arms 112a.

[0030] The first connecting pin 122 is securely pressed into the through hole 121b formed in the coupling arm 121, while a small gap is formed between the circumference of the first connecting pin 122 and the through hole 112b formed in the first arm 112a.

[0031] The other end 121c of the coupling arm 121 is provided with a pair of arms projecting from the end 121a, which is cylindrical in shape, and it carries a second arm 111b therein, which projects from the swashplate 111. The second connecting pin 123, as a connecting device, is inserted into the through-hole 121d formed at the other end 121c of the coupling arm 121 and into a through-hole 111c formed in the second arm 111b, so that the coupling arm 121 and the swashplate 111, which is connected to the coupling arm 121, can rotate relative to each other about a shaft center of the second connecting pin 123. The second connecting pin 123 is securely pressed into the through hole 111c of the second arm 111b, while a small gap is formed between the circumference of the second connecting pin 123 and the through hole 121d formed in the coupling arm 121.

[0032] The coupling mechanism 120 consists of the first arm 112a, the second arm 111b, the coupling arm 121, the first connecting pin 122 and the second connecting pin 123. Therefore, the swashplate 111, which is connected to the rotor 112 attached to the drive shaft 110 by the coupling mechanism 120, can rotate by receiving a torque from the rotor 112, and it can change its inclination along the drive shaft 110. (3) Second connecting pin (design of the inclination)

[0033] The Fig. Figure 5 shows a connected body of the drive shaft 110, the rotor 112, the coupling mechanism 120 and the swashplate 111 when viewed from a position opposite the coupling mechanism 120.

[0034] The line segment with reference symbol P1 designates a plane P1 that contains the axis of the drive shaft 110 and the top dead center (and also the bottom dead center) of the swashplate. The plane P1 corresponds to that in the Fig. The cross-section shown in Figure 1. The top dead center of the swashplate represents a position of the piston 136 at the end of a compression process, while the bottom dead center represents a position of the piston 136 at the end of a suction process. The reference symbol P2 denotes an annular plane P2 of the swashplate 111, while the reference symbol P3 denotes a plane P3 that contains a section line G (a line segment extending from the top to the back of the paper) between plane P1 and plane P2 and is orthogonal to plane P1. If the swashplate 111 is sectioned into two regions by plane P1, the right side is the compression process side, and the left side is the suction process side.

[0035] Any side or surface of the ring-like plane of the swashplate 111 can be defined as a plane P2.

[0036] The Fig. Figure 6 shows the swashplate 111 as viewed from the rotor 112. In the Fig. Reference symbol U denotes a plane U that is orthogonal to the annular plane P2 of the swashplate 111 and contains the top dead center and the midpoint of both side faces of the through-hole 111a, while reference symbol V denotes a plane V that is orthogonal to plane P2 and contains the axis K orthogonal to plane U. The swashplate tilt angle of 0° corresponds to a state in which the line of intersection between plane U and plane V overlaps with the center of the drive shaft 110. Plane U essentially corresponds to plane P1, since the upper side corresponds to the top dead center of the swashplate, while the lower side corresponds to the bottom dead center of the swashplate. The midpoint of the second arm 111b corresponds to plane U.

[0037] As this is the case in the Fig. As shown in Figure 6, an axis m along the axial direction of the through-hole 111c of the second arm 111b is designed such that it is inclined about the point of intersection with the plane U by an axis n, which is orthogonal to the plane U and intersects the axis m at the point of intersection with the plane U. The axis n would run along the axial direction of the through-hole 111c without the angle of inclination α. ​​As shown in the Fig. As shown in Figure 7, the second connecting pin 123, which is firmly pressed against the through-hole 111c, is inclined at an angle α such that one end on the right side is closer to the plane V, while the other end on the left side is farther from the plane V. The angle α is practically less than 0.5°, although it is shown in the Fig. 5 and Fig. Figure 7 is exaggerated. It is preferable that the angle α be set between 0.2° and 1°, preferably between 0.2° and 0.5°.

[0038] Since the second connecting pin 123 is parallel to plane P2 at a swashplate tilt angle of 0°, plane P2 is the same as plane P3 at a tilt angle of 0°, as shown in the Fig. Figure 5 shows that the ring-like plane P2 of the swashplate 111 is orthogonal to the plane P1. (4) Through hole of the swashplate (offset)

[0039] Both ends of the second connecting pin 123 are securely inserted into the through holes 121d of the coupling arm 121, while the through holes 121d of the coupling arm 121 are parallel to the axis n, as shown in the Fig. 6 is shown, and they are also parallel to the axis along the through holes 121b of the coupling arm and also along the through holes 112b of the first arm.

[0040] If the second connecting pin 123 of the connected body, which consists of the drive shaft 110, the rotor 112, the coupling mechanism 120 and the swashplate 111, is tilted, the swashplate 111 rotates counterclockwise about the intersection of the axis m and the axis n, as shown in the Fig. 6 is shown, namely within the gap between the through hole 111a of the swashplate and the circumferential surface of the drive shaft 110, since the second connecting pin 123 is held in the through hole 121d, so that the surface on the side of the suction process of the through hole 111a is brought into contact with the circumferential surface of the drive shaft 110.

[0041] If the circumferential surface of the drive shaft 110 is in contact with the side of the suction process of the through-hole 111a, the applied compression load causes a greater inclination of the swashplate 111, and the distance between the contact point and the point of the compression load becomes greater than in the case of contact on the compression process side, so that the tilting movement of the swashplate could not be carried out gently by the frictional force.

[0042] Accordingly, the axis of the drive shaft 110 is offset by ΔL from the center of both side surfaces of the through hole 111a, as shown in the Fig. 8 is shown.

[0043] The Fig. Figure 8(a) shows a connected body of the drive shaft 110 and the rotor 112 as viewed from the swashplate 111, where the reference numeral T denotes a plane T containing an axis of the drive shaft 110 and parallel to the inner surface (a guide surface which is in contact with the end 121a of the coupling arm) of the first arm 112a.

[0044] The pair of first arms 112a of the rotor 112 is parallel to the plane T, and a distance L1 between the plane T and the guide surface of one end 121a of the coupling arm of the first arm 112a1 on the left side is slightly larger than a distance L2 between the plane T and the guide surface of one end 121a of the coupling arm of the first arm 112a2. The guide surfaces of the pair of first arms 112a are not symmetrical with respect to the plane T, but the center of the guide surfaces of the pair of first arms 112a is offset to the left of the plane T in the drawing by ΔL = (L1-L2) / 2. ΔL is practically less than approximately 0.2 mm, even though this is in the Fig. 8 is exaggerated.

[0045] As this is the case in the Fig. As shown in Figure 8(b), the coupling arm 121 has both sides (contact part) at one end 121a and two guide surfaces of the pair of arms 121c at the second arm 111b, which are provided symmetrically to the center of the coupling arm 121. The center of the coupling arm 121 corresponds to the plane U, as shown in the Fig. 8(c) is shown.

[0046] Therefore, the plane T is offset by ΔL to the left of the center of both sides of the through hole 111a, so that the surface on the side of the compression process of the through hole 111c is in contact with the circumferential surface of the drive shaft 110, even if the second connecting pin 123 is inclined. (5) Tilting movement of the ring-like plane of the swashplate

[0047] The Fig. Figure 9 shows how plane P2 tilts relative to plane P3 when the tilt of the swashplate changes. Fig. 9(a) shows a state of maximum inclination, and the Fig. Figure 9(b) shows another state of minimum inclination. Above the connected body of the drive shaft 110, the rotor 112, the coupling mechanism 120 and the swashplate, the second connecting pin 123 and the swashplate 111, viewed along the direction of an arrow, are shown schematically.

[0048] The second connecting pin 123 is parallel to the plane P2 at the minimum tilt of the swashplate of 0°, and therefore the plane P2 is equal to the plane P3, as shown above right in the Fig. Figure 9(b) shows that the ring-like plane P2 of the swashplate is orthogonal to the plane P1.

[0049] When the swashplate tilt increases to its maximum tilt, as the second connecting pin 123 tilts, as described in the Fig. As shown in Figure 7, the left end part (the suction process side) of the second connecting pin 123 is located in the Fig. 7. a tendency to move away from the rotor's reference level R, while the right end section (compression process side) has a tendency to move close to the reference level R, as shown in the top left of the Fig. Figure 9(a) shows the rotor's reference level R as a support side of bearing 133.

[0050] However, both end parts of the second connecting pin 123 are held in the through-hole 121d of the coupling arm, and therefore the second connecting pin 123 cannot tilt itself beyond the gap between the second connecting pin 123 and the through-hole 121d. As a result, the swashplate 111 tilts in the opposite direction to the tilt of the second connecting pin 123, as shown above right in the Fig. 9(a) is shown.

[0051] The ring-shaped plane P2 of the swashplate tilts at an angle β from plane P3 when it moves in a direction where the outermost part on the compression process side is furthest from the rotor's reference level R, while the outermost part on the suction process side is closest to the rotor's reference level R. Therefore, the angle between plane P2 and plane P3 is zero if the swashplate tilt angle is 0°, and it increases to angle β as the tilt increases to its maximum.

[0052] When the variable displacement compressor 100 actuates the piston 136 to compress a gas, the compression load acts on the swashplate 111 through the piston 136.

[0053] If no compression load is applied, plane P2 tilts away from plane P3, and the compression process side moves away from the rotor's reference level. If a compression load is present, applied by piston 136 to compress a gas, the swashplate 111 tilts, and plane P2 moves close to plane P3. An angle α and also an angle β are designed such that plane P2 of the swashplate becomes nearly equal to plane P3 during operation in the range around the maximum tilt, as shown in the Fig. Figure 10 shows that the compression load increases in a load condition of maximum tilt of the swashplate.

[0054] Thus, plane P2 becomes approximately equal to plane P3 if the variable displacement compressor 100 is operated under a high compression load condition, and therefore the side of the through-hole 111a is in contact with the circumferential surface of the drive shaft 110 in a manner similar to line contact, suppressing any inclination of the through-hole 111a, as described in the Fig. 11 is shown. Therefore, wear of a contact part between the through hole 111a and the circumferential surface of the drive shaft 110 is prevented, and the tilting movement of the swashplate 111 is carried out gently.

[0055] Even if plane P2 is inclined relative to plane P3 when no load is applied, the inclination of the plane decreases as the swashplate inclination decreases, and even the compression load decreases if the swashplate inclination decreases. Therefore, plane P2 approaches plane P3 during operation regardless of the swashplate inclination. Consequently, the side of the through-hole 111a is in contact with the circumferential surface of the drive shaft 110 in a manner similar to line contact, regardless of the swashplate inclination, thus preventing wear on a contact surface between the through-hole 111a and the circumferential surface of the drive shaft 110, and the tilting movement of the swashplate is carried out smoothly.

[0056] Although the example described above shows the coupling mechanism as a connecting device, it is possible that the connecting device is a joint mechanism as disclosed in patent document 2.

[0057] Even though the example described above shows that the first arm of the rotor is offset, it is possible that the coupling arm or the second arm of the swashplate is offset.

[0058] Even if the second connecting pin is inclined by an angle α from the second arm in the example described above, it is possible that the second arm is inclined by an angle α from the plane U to a compaction process area, such that the axis m of the second connecting pin is inclined from the axis n, as is the case in the Fig. Figure 12 shows that in this case, the second connecting pin is orthogonal to the second arm.

[0059] Although the example described above shows a case of a clutchless compressor, it is possible that the compressor is a variable displacement compressor with an electromagnetic clutch, a variable displacement compressor of the wobble plate type, or a variable displacement compressor driven by a motor. INDUSTRIAL APPLICABILITY

[0060] The present invention is applicable to a variable displacement compressor for an air conditioning system for vehicles or the like. REFERENCE MARK LIST 100 compressors 101 cylinder block 101a Cylinder bore 101b Training wall 101c connection path 102 front case 102a Hub part 103 Valve plate 103a, 103b connecting hole 103c opening 104 Cylinder head 104a Suction port 104b Connection path 105 Through bolt 106 Cover element 106a Outlet connection 110 drive shaft 111 Swashplate 111a Through hole 111b second arm 111c Through hole 112 Rotor 112a, 112a1, 112a2 first arm 112b Through hole 114 Inclination reduction spring 115 Inclination magnification spring 116 Spring support element 120 coupling mechanism 121 Coupling arm 121a End of the coupling arm 121b Through hole 121c the other end of the coupling arm 121d Through hole 122 first connecting pin 123 second connecting pin 130 shaft sealing device 131, 132, 133 Warehouse 134 Axial plate 135 Adjusting screw 136 pistons 137 Sliding piece 140 crankcase 141 Suction chamber 142 Outlet chamber 143 Silencer room Path 144, 145 Room 146 200 check valve 300 control valve K axis P1, P2, P3, T, U, V level

Claims

[1] A variable displacement compressor (100) comprising a housing accommodating a discharge chamber (142); a suction chamber (141); a crank chamber (140) and a cylinder bore (101a), a piston (136) provided in the cylinder bore (101a), a drive shaft (110) rotatably supported by the housing, a rotor (112) rotating integrally with the drive shaft (110), a swash plate (111) rotating synchronously with rotation of the rotor (112), which are connected by a connecting device, a converter mechanism converting rotation of the swash plate (111) into reciprocating movement of the piston (136), and a pressure control valve (300) capable of controlling an internal pressure of the crank chamber (140) according to a valve opening, wherein when the valve opening is changed to change the internal pressure of the crank chamber (140), a discharge capacity for compressing and discharging a coolant sucked from the suction chamber (141) into the cylinder bore (101a) is changed by changing a stroke of the piston (136) by changing an inclination of the swash plate (111) to the drive shaft (110) while the swash plate (111) slides on the drive shaft (110), wherein an angle of inclination of the swash plate (111) defines the height of the stroke of the piston (136) and thus the displacement power, characterized by , that, when no compression load is applied to the swash plate (111), the swash plate (111) is connected to be inclined from the rotor (112) such that a compression process region on a side of a positive rotation direction of the swash plate (111) is further spaced from a support side of a thrust bearing formed on the rotor (112) than a suction process region on a side of a negative rotation direction of the swash plate (111) when viewed from a position corresponding to a top dead center of the piston (136), and when a compression load is applied to the swash plate (111), the inclination of the swash plate (111) is suppressed, wherein a plane (P1) containing the axis of the drive shaft (110) and a top dead center and a bottom dead center of the swash plate (111) divides the swash plate (111) into a compression process side and a suction process side, wherein a plane (P3) contains a cutting line (G) between the plane (P1) and an annular plane (P2) of the swash plate (111) and is orthogonal to the plane (P1), wherein the annular plane (P2) of the swash plate (111) inclines by an angle (β) from the plane (P3) when moving in a direction in which the outermost part on the compression process side is furthest away from a reference level (R) of the rotor (112), while the outermost part on the suction process side is closest to the reference level (R) of the rotor (112), where the angle between the plane (P2) and the plane (P3) is zero degrees when the swash plate inclination angle is zero degrees and there is no compression load, and where the angle between the plane (P2) and the plane (P3) is also zero degrees when the swash plate inclination angle is maximum and a compression load is present. [2] The variable displacement compressor (100) according to claim 1, wherein a ratio of a distance of the compression process area of ​​the swash plate (111) from the support side of the thrust bearing to another distance of the suction process area from the support side when viewed from the position corresponding to the top dead center is maximum when the inclination is maximum. [3] A variable displacement compressor (100) according to claim 1 or 2, wherein a minimum inclination angle of the swash plate (111) is set to approximately 0°, and a ratio of a distance of the compression process area of ​​the swash plate (111) from the support side of the thrust bearing to another distance of the suction process area from the support side when viewed from the position corresponding to the top dead center is minimum when the inclination is minimum.

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