JP2011214426A - Compressor with transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor with transmission capable of reducing manufacturing cost and noise.SOLUTION: The transmission mechanism 30 of a compressor is a planetary roller mechanism having a sun roller 14, a plurality of planetary rollers 32, a carrier 9, and a ring roller 33. The ring roller 33 has a first ring part 331 and a second ring part 332. The first ring part 331 is connected to the second ring part 332, to be radially deformable. The first ring part 331 and the second ring part 332 are formed to be tapered so that movement of the second ring part 332 fixing the ring roller 33 makes interferences of the first ring part 331, each planetary roller 32, and the sun roller 14 get larger, and movement of the second ring part 332 releasing the fixing of the ring roller 33 makes the interferences get smaller.

Description

  The present invention relates to a compressor with a transmission.

  Patent Document 1 discloses a conventional compressor with a transmission. The compressor with a transmission includes a housing, a compression mechanism configured in the housing and capable of compressing a refrigerant, an input shaft extending from the outside into the housing and rotatably supported around an axis, and the housing An output shaft that extends in the shaft and is supported so as to be rotatable around the shaft core and can drive the compression mechanism, and is provided between the input shaft and the output shaft in the housing, and transmits the torque of the input shaft to the output shaft. In addition, a speed change mechanism capable of shifting and driving the compression mechanism by increasing / decreasing the rotational speed of the input shaft and transmitting it to the output shaft, and a control mechanism for controlling the speed change mechanism are provided.

  The speed change mechanism is configured by a first planetary gear mechanism provided in front of the axial direction (input shaft side) and a second planetary gear mechanism provided in the rear (output shaft side) in the axial direction. . Each of the first and second planetary gear mechanisms includes a sun gear, a plurality of planetary gears, a carrier that rotatably holds each planetary gear, and a ring gear that meshes with each planetary gear. A thrust bearing and a radial bearing are disposed between each ring gear and the housing, and each ring gear can be fixed or rotated with respect to the housing.

  The control mechanism includes a first one-way clutch provided between the ring gear of the first planetary gear mechanism and the housing, a first clutch provided between the ring gear of the first planetary gear mechanism and the carrier, and a second planetary gear. A second one-way clutch provided between the ring gear of the gear mechanism and the carrier; and a second clutch provided between the ring gear of the second planetary gear mechanism and the housing. The first and second clutches are configured to fix each ring gear to the carrier or the housing by being displaced forward or backward, respectively.

  In the conventional compressor having such a configuration, the first and second clutches individually or simultaneously set the ring gears in the fixed state or release the fixed state. Then, the first and second one-way clutches allow or restrict relative rotation between each ring gear and the housing or the carrier. As a result, the transmission means can drive the compression mechanism by shifting the compression mechanism stepwise.

JP 2007-107412 A

  By the way, the conventional compressor with a transmission has a problem that the manufacturing cost increases due to its complicated structure, and noise due to vibration is large.

  An object of the present invention is to provide a compressor with a transmission capable of realizing a reduction in manufacturing cost and noise.

A compressor with a transmission according to the present invention includes a housing, a compression mechanism configured in the housing and capable of compressing a refrigerant, and an input extending from the outside into the housing and supported rotatably around an axis. A shaft, an output shaft that extends in the housing, is rotatably supported around the shaft core and can drive the compression mechanism, and is provided between the input shaft and the output shaft in the housing. The torque of the input shaft can be transmitted to the output shaft while the rotational speed of the input shaft is kept constant or increased and transmitted to the output shaft to shift the compression mechanism in two stages. And a control mechanism for controlling the transmission mechanism,
The speed change mechanism is a planetary roller mechanism having a sun roller, a plurality of planetary rollers, a carrier and a ring roller;
The carrier can rotate integrally with the input shaft while rotatably holding the planetary rollers,
The sun roller can rotate integrally with the output shaft while being in contact with the planetary rollers.
The ring roller is configured to be capable of being fixed and rotated with respect to the housing by moving in a direction parallel to the shaft core with respect to the housing while being in contact with the planetary rollers.
The control mechanism is provided between the carrier and the ring roller, allows a relative rotation in one direction between the carrier and the ring roller and restricts relative rotation in the other direction, and the housing. A clutch provided between the ring roller and the clutch for restricting the rotation of the ring roller by engagement;
The clutch is formed between the housing and the ring roller, and is formed on the housing toward the ring roller, and a friction layer that fixes the ring roller to the housing by the movement of the ring roller. A control chamber, a control piston movably accommodated in the control chamber, a thrust bearing provided between the control piston and the ring roller, and supplying control pressure to the control chamber to control the control piston. A pressure adjusting means for moving,
The ring roller is in contact with each planetary roller and provided with the friction layer, and is rotatable with the first ring portion and movable in a direction parallel to the axis. A second ring portion for supporting the clutch,
The first ring portion is connected to the second ring portion so as to be deformable in a radial direction,
In the first ring portion and the second ring portion, the tightening margin of the first ring portion, each planetary roller, and the sun roller is increased by the movement of the second ring portion that fixes the ring roller, and the ring roller It is formed in a taper shape so that the tightening allowance is reduced by the movement of the second ring portion for releasing the fixing (Claim 1).

  The compressor with a transmission according to the present invention (hereinafter simply referred to as “compressor”) employs a planetary roller mechanism as a transmission mechanism. For this reason, unlike the case where the planetary gear mechanism in which each planetary gear tooth and the ring gear tooth collide with each other and the vibration caused by the collision of each planetary gear tooth and the sun gear tooth as the speed change mechanism, It is hard to generate vibration. For this reason, low noise is realized in this compressor.

  Further, in this compressor, a contact load is required between the sun roller and each planetary roller and between each planetary roller and the ring roller in order to transmit torque. Need to give. Therefore, the ring roller is easily deformed by the sun roller and each planetary roller. On the other hand, in this compressor, a one-way clutch is provided between the carrier and the ring roller in order to switch between constant speed and speed increase, and the carrier becomes an inner ring of the one-way clutch and the ring roller becomes an outer ring of the one-way clutch. . In order for the one-way clutch to function correctly, the inner ring and the outer ring require high accuracy in terms of dimensions, cylindricity, etc., and deformation of the ring roller impairs the function of the one-way clutch. In that case, it is difficult to shift the compression mechanism in two stages.

  In this regard, in the compressor of the present invention, the ring roller that can move in the direction parallel to the shaft center with respect to the housing has the first ring portion and the second ring portion. The first ring portion is in contact with each planetary roller and provided with a friction layer, and is connected to the second ring portion so as to be deformable in the radial direction. For this reason, the first ring portion is deformed in the radial direction by a tightening allowance provided between the sun roller and each planetary roller and between each planetary roller and the ring roller. Further, the second ring portion is rotatable with the first ring portion and movable in a direction parallel to the shaft center without being affected by the radial displacement of the first ring portion, and supports the one-way clutch. For this reason, even if the first ring portion is displaced in the radial direction, the second ring portion maintains high accuracy such as dimensions and cylindricity, and does not impair the function of the one-way clutch.

  And in this compressor, the 1st ring part and the 2nd ring part are formed in taper shape. For this reason, if the 2nd ring part moves so that a ring roller may be fixed, the interference of the 1st ring part, each planetary roller, and a sun roller will become large. At this time, the carrier and the second ring portion are allowed to rotate relative to each other in one direction by the one-way clutch of the control mechanism, and the output shaft enters a speed-up rotation state in which the rotation speed is increased with respect to the input shaft.

  Further, if the second ring portion moves so as to release the fixing of the ring roller, the tightening allowance of the first ring portion, each planetary roller, and the sun roller becomes small. At this time, relative rotation of the carrier and the second ring portion in the other direction is restricted by the one-way clutch of the control mechanism, and the output shaft is in a constant speed rotation state where the rotation speed remains constant with respect to the input shaft.

  For this reason, since this compressor can change the compression mechanism in two stages and the structure is simplified, the manufacturing cost can be reduced.

  Therefore, the compressor with a transmission according to the present invention can realize low manufacturing cost and low noise.

  Further, in this compressor, the tightening margin is increased when the transmitted torque is increased, and the tightening margin is decreased when the transmitted torque is small. For this reason, the interference is changed according to the torque to be transmitted and the power loss is also changed, so that power saving can be realized. If the second ring portion is configured to be pushed by the discharge pressure, the second ring portion can be pushed with a high discharge pressure at the time of acceleration, and torque can be reliably transmitted with a large tightening allowance.

  The second ring part preferably has higher rigidity than the first ring part (claim 2). In other words, it is preferable that the first ring portion has lower rigidity than the second ring portion. In this case, it is easy for the first ring portion to give a tightening margin between the sun roller and each planetary roller and between each planetary roller and the ring roller, and the one-way clutch easily functions correctly.

  The first ring portion, each planetary roller, and the sun roller have a larger tightening allowance due to the movement of the second ring portion that fixes the ring roller, and a smaller allowance due to the movement of the second ring portion that releases the fixing of the ring roller. Preferably, it is formed in a taper shape.

  In this case, the tightening margin is increased when the transmitted torque is increased, and the tightening margin is decreased when the transmitted torque is small.

  It is preferable that a biasing member for biasing the ring roller is provided between the housing and the first ring portion so as to reduce the tightening allowance. As the urging member, it is possible to employ an elastic rubber in addition to a spring such as a leaf spring.

  In this case, since the power loss is reduced by the urging member, the compressor reliably saves power in the operating state other than during acceleration.

It is a longitudinal cross-sectional view of the compressor with a transmission of Example 1. FIG. 1 is an enlarged longitudinal sectional view of a main part of a compressor with a transmission according to Embodiment 1. FIG. It is a principal part expanded horizontal sectional view of the compressor with a transmission of Example 1. FIG. It is a longitudinal cross-sectional view of the compressor with a transmission of Example 2. It is a principal part expansion longitudinal cross-sectional view of the compressor with a transmission of Example 2. FIG.

  Embodiments 1 and 2 embodying the present invention will be described below with reference to the drawings.

Example 1
As shown in FIG. 1, the compressor with a transmission according to the first embodiment (hereinafter simply referred to as “compressor”) is a combination of a scroll type compression mechanism 20 and a speed change mechanism 30 and a control mechanism 40. For example, it is mounted on a vehicle and constitutes an air conditioner. In each figure, the input shaft 1 side (left side of the drawing) is defined as the front side, and the output shaft 2 side (right side of the drawing) is defined as the rear side, and the front-rear direction is displayed.

  The compressor includes a housing 10 in which a first housing member 3, a second housing member 4, a third housing member 5, and a fourth housing member 6 are integrally fastened in this order. The rear end surface of the first housing member 3 and the front end surface of the second housing member 4 are brought into contact with each other and fastened together to form a transmission chamber 10a. The transmission chamber 10a is filled with traction oil. The first housing member 3 is formed with a flow path 3a for guiding traction oil existing in the outer peripheral area to the inner peripheral area in the speed change chamber 10a.

  The 3rd housing member 5 has the fixed scroll 21 mentioned later integrally. Between the second housing member 4 and the third housing member 5, a movable scroll 22, which will be described later, is accommodated. As the third housing member 5 and the fourth housing member 6 are fastened to each other, a suction chamber 28 and a discharge chamber 29 are formed inside.

  The input shaft 1 is supported on the boss of the first housing member 3 through the seal member 7 and the bearing device 8 so as to be rotatable around the axis O1. Although the first housing member 3 and the bearing device 8 are press-fitted, a gap is secured between the bearing device 8 and the input shaft 1. By this gap and the key 15, an assembly S composed of the input shaft 1, the carrier 9, the radial bearing 31, each planetary roller 32, the sun roller 14, the ring roller 33, the friction layer 35, the circlip 34 a and the one-way clutch 34 is formed. The first housing member 3 is movable in a direction parallel to the axis O1.

  The rear end of the input shaft 1 protrudes rearward in the speed change chamber 10a, and in the middle of the input shaft 1 faces the first housing member 3 with a gap and extends in a disk shape in the radially outward direction. The main body 9a is integrally formed. The carrier body 9a constitutes a speed change mechanism 30 described in detail later.

  In the boss of the second housing member 4, the output shaft 2 is supported through a seal member 11 and a radial bearing 12 so as to be rotatable around the axis O <b> 1. The front end of the output shaft 2 is located in the carrier body 9 a of the input shaft 1, and a radial bearing 13 is also provided between the carrier body 9 a and the output shaft 2. The input shaft 1 is formed with a flow path 1 a that communicates with the flow path 3 a formed in the first housing member 3 and extends to the radial bearing 13. The output shaft 2 is provided with a sun roller 14 located behind the carrier body 9a. A key 15 is provided between the output shaft 2 and the sun roller 14 so that the sun roller 14 can rotate integrally with the output shaft 2 and can move in a direction parallel to the axis O1 with respect to the output shaft 2. It has been. The sun roller 14 also constitutes a speed change mechanism 30 described in detail later. The rear end of the output shaft 2 extends rearward toward the movable scroll 22.

  Next, the compression mechanism 20 will be described. A drive bush 23 and a movable scroll 22 integral with the balancer are accommodated between the second housing member 4 and the third housing member 5.

  The drive bushing 23 is fixed in an eccentric state at the rear end of the output shaft 2 and can rotate integrally with the output shaft 2. A radial bearing 24 is disposed on the outer peripheral surface of the drive bush 23.

  The movable scroll 22 includes a boss 22a rotatably supported by the drive bush 23 via a radial bearing 24, a disk-like movable side plate 22b that is integrated with the boss 22a and extends in the radial direction, and the movable side plate 22b. And a spiral movable spiral part 22c protruding in parallel with the axis O1 from the rear to the rear.

  Three or more fixing pins 25a are fixed to the rear surface of the second housing member 4 in parallel with the axis O1. Further, the same number of movable pins 25b as the fixed pins 25a are fixed to the movable side plate 22b of the movable scroll 22 in parallel with the axis O1. Furthermore, the same number of movable rings 25c as the fixed pins 25a and the movable pins 25b are disposed between the second housing member 4 and the movable side plate 22b. A through-hole 25d is formed in the movable ring 25c, and a pair of fixed pin 25a and movable pin 25b are accommodated in the through-hole 25d in a state where the revolving distance of the movable scroll 22 is between the respective shaft centers. Has been. These fixed pin 25a, movable pin 25b, and movable ring 25c constitute a rotation prevention means 25 that prevents the movable scroll 22 from rotating.

  The third housing member 5 has a fixed scroll 21 integrally therewith. The fixed scroll 21 includes a disk-shaped fixed side plate 21b that extends in the radial direction, and a spiral fixed spiral portion 21c that protrudes forward from the fixed side plate 21b in parallel with the axis O1.

  The fixed spiral portion 21c of the fixed scroll 21 and the movable spiral portion 22c of the movable scroll 22 are set to have the same protruding length in the direction of the axis O1. The fixed spiral portion 21 c of the fixed scroll 21 slides with the movable side plate 22 b of the movable scroll 22, and the movable spiral portion 22 c of the movable scroll 22 slides with the fixed side plate 21 b of the fixed scroll 21.

  A discharge port 29a is provided through the central portion of the fixed side plate 21b so as to be able to communicate with the discharge chamber 29. In the discharge chamber 29, a discharge valve 26 and a retainer 27 are fixed to the fixed side plate 21b so as to close the discharge port 29a. Further, a suction port 28a communicating with the suction chamber 28 is provided through the outer peripheral portion of the fixed side plate 21b.

  The above-described second to fourth housing members 4, 5, 6, the output shaft 2, the drive bush 23, the movable scroll 22, the rotation prevention means 25, the fixed scroll 21, and the like constitute a scroll type compression mechanism 20.

  The discharge chamber 29 is connected to a condenser 42 via a pipe 41, the condenser 42 is connected to an evaporator 45 via an expansion valve 44 via a pipe 43, and the evaporator 45 is connected to the suction chamber 28 via a pipe 46. Has been. The discharge chamber 29 is provided with a discharge pressure supply passage (path Pd-Pd shown in FIG. 1) for supplying a discharge pressure Pd in the discharge chamber 29 to a flow path switching electromagnetic valve 61 described later. Further, the suction chamber 28 is provided with a suction pressure supply passage (path Ps-Ps shown in FIG. 1) for supplying the suction pressure Ps in the suction chamber 28 to the flow path switching electromagnetic valve 61. Further, although not shown, a communication passage is provided between the second and third housing members 4 and 5 for connecting the suction chamber 28 and the transmission chamber 10a to maintain the pressure in the transmission chamber 10a at the suction pressure Ps. ing.

  Next, the speed change mechanism 30 will be described. In the speed change chamber 10a, four support shafts 9b are provided projecting toward the rear on the circumference centered on the axial center O1 imaginary on the outer peripheral side of the rear surface of the carrier body 9a. Each support shaft 9b is a cylindrical shaft body. A planetary roller 32 is rotatably supported by each support shaft 9a one by one via a radial bearing 31. The outer peripheral surfaces of the four planetary rollers 32 are in contact with the outer peripheral surface of the sun roller 14 with an allowance. The outer peripheral surface of each planetary roller 32 and the outer peripheral surface of the sun roller 14 are also coated to prevent relative slip.

  A rear carrier 9d is fixed to the rear end of each support shaft 9b. The rear carrier 9d has a substantially cylindrical shape extending rearward. The carrier body 9a, the support shafts 9b, and the rear carrier 9d constitute a carrier 9 that can rotate integrally with the input shaft 1 while rotatably supporting the four planetary rollers 32.

  Between each planetary roller 32 and the first and second housing members 3, 4, a ring roller 33 is disposed that can move relative to the housing 10 in a direction parallel to the axis O 1. As illustrated in FIG. 2, the ring roller 33 includes a cylindrical first ring portion 331 and a cylindrical second ring portion 332.

  The first ring portion 331 is made of a material having relatively low rigidity, and as shown in FIG. 3, displacement in the radial direction is allowed. For this reason, the first ring portion 331 can be displaced in the radial direction by a tightening allowance provided between the sun roller 14 and each planetary roller 32 and between each planetary roller 32 and the ring roller 33. The inner peripheral surface of the first ring portion 331 is also coated to prevent relative slip.

  As shown in FIG. 2, a first rear end surface 331a located on the inner peripheral side and a second rear end surface 331b located on the outer peripheral side are formed at the rear end of the first ring portion 331. The first rear end surface 331a is formed in a tapered shape having a small diameter on the inner peripheral surface side and a large diameter on the outer peripheral surface side. The second rear end surface 331b is formed perpendicular to the axis O1. The first ring portion 331 has a step portion 331c so that the second rear end surface 331b protrudes rearward from the first rear end surface 331a. A pin hole 331d extending in the radial direction is provided through the step portion 331c.

  The second ring portion 332 is made of a material having a relatively high rigidity. For this reason, as shown in FIG. 1, the outer peripheral surface of the one-way clutch 34 is in contact with the inner peripheral surface of the second ring portion 332.

  As shown in FIG. 2, a first front end surface 332a located on the inner peripheral side and a second front end surface 332b located on the outer peripheral side are formed at the front end of the second ring portion 332. The first front end surface 332a is formed in a tapered shape having a small diameter on the inner peripheral surface side and a large diameter on the outer peripheral surface side, and is aligned with the first rear end surface 331a. The second front end face 332b is formed perpendicular to the axis O1. The second ring portion 332 has a step portion 332c so that the first front end surface 332a protrudes forward from the second front end surface 332b. A pin hole 332d extending in the radial direction is provided in the step portion 332c.

  A stepped pin 333 is fitted in the pin hole 331 d of the first ring portion 331 and the pin hole 332 d of the second ring portion 332. The head of the pin 333 is press-fitted into the pin hole 331d, and the shaft portion of the pin 333 is loosely fitted into the pin hole 332d. In this state, the first rear end surface 331a of the first ring portion 331 and the first front end surface 332a of the second ring portion 332 are in contact with each other. There is a gap between the second rear end surface 331b of the first ring portion 331 and the second front end surface 332b of the second ring portion 332.

  For this reason, the second ring portion 332 supports the one-way clutch 34 and can move together with the first ring portion 331 in a direction parallel to the axis O1 without being affected by the radial displacement of the first ring portion 331. Is possible. For this reason, even if the first ring portion 331 is displaced in the radial direction, the second ring portion 332 maintains high accuracy such as dimensions and cylindricity, and the function of the one-way clutch 34 is not impaired.

  As shown in FIG. 1, the sun roller 14, each planetary roller 32, the ring roller 33, and the carrier 9 constitute a speed change mechanism 30 that is a planetary roller mechanism.

  A one-way clutch 34 is fixed to the outer peripheral surface of the rear carrier 9d by a circlip 34a. The one-way clutch 34 is a known general-purpose product, and restricts relative rotation in the other direction while allowing relative rotation in one direction of the ring roller 33 with respect to the carrier 9. In the present embodiment, the direction in which the input shaft 1 and the carrier 9 rotate around the axis O1 is set clockwise when the compressor is viewed from the front. The one-way clutch 34 allows the ring roller 33 to rotate relative to the carrier 9 in the counterclockwise direction, while restricting the ring roller 33 from rotating relative to the carrier 9 in the clockwise direction. It is arranged.

  A friction layer 35 is provided on the front surface of the ring roller 33 toward the rear surface of the first housing member 3. The friction layer 35 is an annular flat plate made of a material having low slidability. As will be described later, when the ring roller 33 moves forward, the friction layer 35 comes into contact with the rear surface of the first housing member 3.

  A control chamber 36 is recessed in the second housing member 4 at a position facing the rear surface of the ring roller 33. An annular control piston 37 is accommodated in the control chamber 36 so as to be movable in the front-rear direction (in the direction of the axis O1). Rubber O-rings 38 a and 38 b that seal between the control piston 37 and the control chamber 36 are attached to the inner peripheral surface and the outer peripheral surface of the control piston 37.

  The control chamber 36 is connected to a flow path switching electromagnetic valve 61 as pressure adjusting means via a flow path 36a. The flow path switching electromagnetic valve 61 switches and connects the control chamber 36 to the discharge pressure supply passage (path Pd-Pd shown in FIG. 1) or the suction pressure supply path (path Ps-Ps shown in FIG. 1). Yes. As described above, the pressure in the transmission chamber 10a facing the control piston 37 is held at the suction pressure Ps. A thrust bearing 39 is accommodated in the front portion of the control piston 37.

  The friction layer 35, the control chamber 36, the control piston 37, the flow path 36a, the flow path switching electromagnetic valve 61, and the like constitute a clutch 60 that fixes or rotates the ring roller 33 with respect to the first housing member 3. The control mechanism 40 is configured by the clutch 60, the one-way clutch 34, the flow path switching electromagnetic valve 61, the flow path 36a, and the like.

  An electromagnetic clutch 50 is connected to the front end of the input shaft 1. The electromagnetic clutch 50 is fixed to the front end of the first housing member 3, a disc-shaped hub 51 fixed to the front end of the input shaft 1 so as to be integrally rotatable, an armature 53 connected to the hub 51 by a leaf spring 52, and the like. And a coil 54. A pulley 56 is rotatably supported on the boss of the first housing member 3 via a radial bearing 55. A belt (not shown) connected to an engine or the like as an external drive source is wound around the pulley 56. The coil 54 is disposed in the pulley 56.

  In the compressor of the embodiment configured as described above, when the coil 54 of the electromagnetic clutch 50 is energized, the armature 53 is magnetically attached to the pulley 56 against the elastic force of the leaf spring 52, and the input The shaft 1 rotates integrally with the pulley 56, and torque is applied to the input shaft 1. If the input shaft 1 is rotationally driven around the axis O <b> 1, the rotation of the input shaft 1 is transmitted to the output shaft 2 at a constant speed or increased by the speed change mechanism 30.

  On the other hand, when the energization of the coil 54 is stopped, the armature 53 is separated from the pulley 56 by the elastic force of the leaf spring 52, and the application of torque to the input shaft 1 is interrupted. Thus, the driving force from the outside is connected to and disconnected from the input shaft 1 by the electromagnetic clutch 50.

  In the compression mechanism 20, when the output shaft 2 is driven to rotate, the drive bush 23 rotates eccentrically with its own axis, and the orbiting of the movable scroll 22 is restricted by the rotation preventing means 25. To do. Thereby, the volume of the compression chamber formed between the fixed scroll 21 and the movable scroll 22 is reduced from the outer peripheral side toward the central portion. For this reason, the refrigerant in the suction chamber 28 is compressed in the compression chamber and discharged into the discharge chamber 29. The refrigerant in the discharge chamber 29 is supplied to the condenser 42, and cooling of the vehicle is realized by the evaporator 45.

  During this time, when the discharge pressure Pd is applied to the control chamber 36, the pressure in the control chamber 36 becomes higher than the pressure in the transmission chamber 10a, and the control piston 37 moves forward. Then, the control piston 37 moves the second ring part 332 in the forward direction, the second ring part 332 moves the first ring part 331 in the forward direction, and moves the first ring part 331 with respect to the first housing member 3. Press. Then, the control piston 37 integrally pushes the assembly S through the ring roller 33 in the forward direction. For this reason, since a frictional force acts between the friction layer 35 and the first housing member 3, the ring roller 33 is fixed to the first housing member 3.

  At this time, in this compressor, since the first front end surface 332a of the second ring portion 332 biases the first rear end surface 331a of the first ring portion 331 toward the axis O1, the first ring portion 331 and each planet The tightening margin between the rollers 32 and between each planetary roller 32 and the sun roller 14 is increased.

  In the one-way clutch 34, the ring roller 33 rotates relative to the carrier 9 in one direction (when the compressor 1 is viewed from the front, the ring roller 33 rotates relative to the carrier 9 counterclockwise. ) Is allowed. Therefore, each planetary roller 32 that revolves clockwise around the axis O1 as the input shaft 1 and the carrier 9 rotate is counterclockwise around each support shaft 9b due to the interference with the first ring portion 331. Rotate to As a result, the sun roller 14 that contacts each planetary roller 32 and the output shaft 2 that rotates integrally with the sun roller 14 are in a speed-up rotation state in which the rotation of the input shaft 1 is increased and transmitted.

  On the other hand, when the suction pressure Ps is applied to the control chamber 36, the pressure in the control chamber 36 becomes equal to the pressure in the transmission chamber 10a, and the control piston 37 presses the ring roller 33 against the first housing member 3. Disappear. The control piston 37 does not push the assembly S forward through the ring roller 33. Then, the friction layer 35 and the first housing member 3 are separated from each other, so that the friction force does not act between them, and the ring roller 33 can be rotated with respect to the first housing member 3. In this state, the ring roller 33 rolls on the thrust bearing 39.

  At this time, in this compressor, since the first front end surface 332a of the second ring portion 332 allows the first rear end surface 331a of the first ring portion 331 to bulge in the radially outward direction, The interference between the planetary rollers 32 and between each planetary roller 32 and the sun roller 14 is reduced.

  In this compressor, the ring roller 33 tries to rotate around the axis O1 in the clockwise direction as the input shaft 1 rotates. As each planetary roller 32 in contact with the sun roller 14 rotates in the clockwise direction, the ring roller 33 attempts to pass the input shaft 1 relatively in the clockwise direction. In the one-way clutch 34, the ring roller 33 rotates relative to the carrier 9 in the other direction (the ring roller 33 rotates relative to the carrier 9 in the clockwise direction when the compressor is viewed from the front). regulate. The thrust bearing 39 prevents the ring roller 33 from being dragged with respect to the control piston 37. As a result, the input shaft 1, the carrier 9, each planetary roller 32, the sun roller 14, the ring roller 33 and the output shaft 2 rotate together, and the rotation of the input shaft 1 is transmitted to the output shaft 2 at a constant speed, etc. It will be in a fast rotation state.

  Thus, in this compressor, since the speed change mechanism 30 including a planetary roller mechanism is employed, vibration is hardly generated and low noise is realized. In addition, since the compressor can change the compression mechanism 20 in two steps, the structure is simplified, so that the manufacturing cost can be reduced.

  Therefore, this compressor can realize a reduction in manufacturing cost and low noise.

  Further, in this compressor, the tightening margin is increased when the transmitted torque is increased, and the tightening margin is decreased when the transmitted torque is small. For this reason, the interference is changed according to the torque to be transmitted and the power loss is also changed, so that power saving can be realized. Further, since the second ring portion 332 is pushed by the discharge pressure Pd, the second ring portion 332 can be pushed by the high discharge pressure Pd at the time of acceleration, and torque can be reliably transmitted with a large tightening allowance. is there.

(Example 2)
In the compressor according to the second embodiment, as illustrated in FIGS. 4 and 5, the ring roller 72 includes a first ring portion 721, a second ring portion 332, and a pin 333.

  As shown in FIG. 5, the inner peripheral surface 721e of the first ring portion 721 is formed in a tapered shape with a large diameter at the front and a small diameter at the rear. At the rear end of the first ring portion 721, a first rear end face 721a located on the inner peripheral side and a second rear end face 721b located on the outer peripheral side are formed. The first rear end surface 721a is formed in a tapered shape having a small diameter on the inner peripheral surface side and a large diameter on the outer peripheral surface side. The first front end surface 332a of the second ring portion 332 is aligned with the first rear end surface 721a.

  Further, the outer peripheral surface 71a of each planetary roller 71 is formed in a tapered shape with a large diameter at the front and a small diameter at the rear. The outer peripheral surface 73a of the sun roller 73 is formed in a tapered shape with a small diameter at the front and a large diameter at the rear.

  An outer flange 721f extending radially outward is formed at the front end of the first ring portion 721, and a plate that urges the ring roller 72 rearward between the first housing member 3 and the outer flange 721f. A spring 74 is provided. The leaf spring 74 is an urging member. The first housing member 3 is provided with a friction layer 75 at a position facing the leaf spring 74. The flow path 3 a formed in the first housing member 3 extends into the friction layer 75. Other configurations are the same as those of the first embodiment, and the same configurations are denoted by the same reference numerals and detailed description thereof is omitted.

  In this compressor, when the control piston 36 pushes the second ring portion 332 forward by the discharge pressure Pd, the interference between the first ring portion 721, each planetary roller 71 and the sun roller 73 becomes larger. In other words, the tightening margin increases when the transmitted torque is increased.

  Conversely, if the second ring portion 332 moves rearward, the tightening allowance between the first ring portion 721, each planetary roller 71, and the sun roller 73 becomes smaller. That is, the tightening margin is reduced when the transmitted torque is small and at a constant speed.

  Further, this compressor is configured so that the power loss is reduced by the leaf spring 74, so that the operation state other than the time of acceleration is reliably saved. Other functions and effects are the same as those of the first embodiment.

  In the above, the present invention has been described with reference to the first and second embodiments. However, the present invention is not limited to the first and second embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  The compression mechanism is not limited to the scroll type, and a general compression mechanism can be adopted. Further, the clutch may have, for example, a link mechanism in which a plurality of movable members are combined.

  The present invention is applicable to a vehicle air conditioner.

DESCRIPTION OF SYMBOLS 10 ... Housing 20 ... Compression mechanism (scroll type compression mechanism)
O1 ... shaft core 1 ... input shaft 2 ... output shaft 30 ... speed change mechanism (planetary roller mechanism)
DESCRIPTION OF SYMBOLS 40 ... Control mechanism 14, 73 ... Sun roller 32, 71 ... Planetary roller 9 ... Carrier 33, 72 ... Ring roller 34 ... One-way clutch 60 ... Clutch 331, 721 ... 1st ring part 332 ... 2nd ring part 35, 75 ... Friction Layer 36 ... Control chamber 37 ... Control piston 39 ... Thrust bearing 61 ... Pressure adjusting means (flow path switching solenoid valve)
74 ... Leaf spring (biasing member)

Claims (4)

A housing; a compression mechanism configured in the housing and capable of compressing the refrigerant; an input shaft extending from the outside into the housing and supported rotatably around an axis; and extending into the housing. An output shaft that is rotatably supported around the shaft core and can drive the compression mechanism, and is provided between the input shaft and the output shaft in the housing, and the torque of the input shaft is transmitted to the output shaft. A transmission mechanism capable of shifting and driving the compression mechanism in two stages by transmitting the rotation speed of the input shaft to the output shaft while maintaining or increasing the rotational speed of the input shaft while controlling the transmission mechanism. And a control mechanism for
The speed change mechanism is a planetary roller mechanism having a sun roller, a plurality of planetary rollers, a carrier and a ring roller;
The carrier can rotate integrally with the input shaft while rotatably holding the planetary rollers,
The sun roller can rotate integrally with the output shaft while being in contact with the planetary rollers.
The ring roller is configured to be capable of being fixed and rotated with respect to the housing by moving in a direction parallel to the shaft core with respect to the housing while being in contact with the planetary rollers.
The control mechanism is provided between the carrier and the ring roller, allows a relative rotation in one direction between the carrier and the ring roller and restricts relative rotation in the other direction, and the housing. A clutch provided between the ring roller and the clutch for restricting the rotation of the ring roller by engagement;
The clutch is formed between the housing and the ring roller, and is formed on the housing toward the ring roller, and a friction layer that fixes the ring roller to the housing by the movement of the ring roller. A control chamber, a control piston movably accommodated in the control chamber, a thrust bearing provided between the control piston and the ring roller, and supplying control pressure to the control chamber to control the control piston. A pressure adjusting means for moving,
The ring roller is in contact with each planetary roller and provided with the friction layer, and is rotatable with the first ring portion and movable in a direction parallel to the axis. A second ring portion for supporting the clutch,
The first ring portion is connected to the second ring portion so as to be deformable in a radial direction,
In the first ring portion and the second ring portion, the tightening margin of the first ring portion, each planetary roller, and the sun roller is increased by the movement of the second ring portion that fixes the ring roller, and the ring roller A compressor with a transmission, wherein the compressor is formed in a tapered shape so that the tightening margin is reduced by the movement of the second ring portion for releasing the fixing.   The compressor with a transmission according to claim 1, wherein the second ring portion has higher rigidity than the first ring portion.   The first ring portion, each planetary roller, and the sun roller have a larger tightening margin due to the movement of the second ring portion that fixes the ring roller, and the movement of the second ring portion that releases the fixation of the ring roller. The compressor with a transmission according to claim 1 or 2, wherein the compressor is formed in a tapered shape so as to reduce a tightening margin.   The compressor with a transmission according to claim 3, wherein a biasing member that biases the ring roller is provided between the housing and the first ring portion so as to reduce a tightening margin.

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