JPH04194375A - Compressor with transmission - Google Patents

Abstract

PURPOSE:To simplify the structure of an automatic pressure regulating cam mechanism for a friction pulley by installing each of tangential cam grooves on the surface of a rotational member being opposed to a friction type continuously variable transmission clamped to a compressor part, and holding a ball between these cam grooves. CONSTITUTION:A compressor and a friction type continuously variable transmission are solidly connected to each other, supporting an output disk 5 on an input shaft free of rotation, and it is connected to an output shaft via an automatic pressure regulating cam mechanism 20. This automatic pressure regulating cam mechanism 20 consists of a cam disk 21, the output disk 5 and a ball held between both these disks. A cam groove 31 is installed on the back of the output disk 5 and another cam groove 32 on the back of the cam disk 21 in the tangential direction of a virtual circle 33, respectively, and both ends of each cam groove are shallowed. The ball is correctly held in a position aright owing to the groove alone, so a retainer or the like becomes disused, thus the structure is simplified as a whole.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention provides a compressor suitable for use as a refrigerant compressor for, for example, automobile air conditioning, in particular, by providing a continuously variable transmission section on the input side. The present invention relates to a compressor of this type in which the discharge amount of compressed fluid can be changed steplessly.

[Conventional technology]

For example, in refrigerant compressors for automobile air conditioning, in order to change the discharge amount steplessly, a swash plate type compressor is used to make the angle of inclination of the swash plate variable, and the discharge amount of the compressor itself is Even if the output rotation speed is constant, attempts have already been made to insert a friction-type continuously variable transmission into the shaft that drives the compressor and drive the compressor at variable speeds, and the output rotation speed varies significantly depending on the driving condition of the car. It is now possible to obtain a comfortable cooling feeling by eliminating fluctuations in cooling capacity and waste of power that occur when an air conditioning refrigerant compressor is driven by a driving engine.

Friction-type continuously variable transmissions are of the type called "Ring Cone" (registered trademark), in which a metal ring is engaged with a metal conical friction wheel. A device that performs continuously variable speed by changing the combined radius is known. In particular, a large number of conical friction wheels are supported around an input shaft so that they can rotate and revolve around an input shaft, and they are caused to move planetarily. A common ring is engaged with a type friction wheel (called a planetary cone), and by moving the ring and changing the engagement point, the revolution speed of the planetary cone is changed, and the output disk that moves with the planetary cone is connected to the output shaft. Those that extract rotation that is continuously variable in speed use a large number of planetary cones and have many engagement points with rings, etc., so they can transmit a large amount of power, and because they are planetary, they have a wide speed change range. Therefore, it can be used to drive a refrigerant compressor for automobile air conditioning.

In addition, although it is not a planetary type, there is a long-known continuously variable transmission called a "half toroidal transmission", in other words, a pair of hollow donut-shaped rings cut in two and facing each other. friction wheel and several intermediate friction wheels bridging between them, and by tilting the axes of these intermediate friction wheels at the same angle, the human power shaft is connected to one of the friction wheels. A device in which the rotational speed of an output shaft connected to the other friction wheel can be changed steplessly with respect to the rotation of the other friction wheel can also be used for the same purpose because the transmitted power is relatively large.

In addition to these, many types of friction-type continuously variable transmissions are known, but in any case, friction wheels are used mutually, or a friction wheel and a ring (the ring can be considered a type of friction wheel). Since it is necessary to generate an appropriate amount of friction force depending on the size of the transmitted power, that is, the load torque, on the friction engagement surface with the Self-regulating pressure dam devices are often used.

FIGS. 9 and 10 illustrate a conventional self-adjusting pressure ram device, which includes a friction wheel (such as an output disk, generally referred to as a "rotating member") that can move in the axial direction. , and a cam disk or the like (referred to as "the other rotating member") that is fixed to the output shaft and rotates but does not move in the axial direction to support it in the axial direction.

That is, in FIGS. 9 and 10, reference numeral 201 denotes an inner arc-shaped cam groove provided in one rotating member 200;
02 is deep, and both curved end portions 203 and 204 have a shape that becomes gradually shallower and narrower in width. Opposed to the cam groove 201, the other rotating member 205 has a cam groove 2.
06 is provided, and the cam groove 206 is the aforementioned cam groove 2.
01, the center portion 207 is deep and the curved ends 208 and 209 are gradually shallower. And the cam groove 201 of the two opposing rotating members and the cam? A ball 210 is held between R206 and R206.

In this example, the center of the cam grooves 201 and 206! 2
11 is a circular arc having a radius γ centered on the axis 0 of an input shaft and an output shaft (not shown).

When the speed-changed rotation is taken out from the input shaft to the output shaft via the continuously variable transmission, the torque T is generated by one rotating member 200.
It is transmitted from the rotary member 205 to the other rotating member 205 via the ball 210. Therefore, since the tangential force F due to the torque T acts, the two rotating members 200 and 205 are shifted around the axis 0 mainly by the amount of play, and take a shift angle α.

As a result, the ball 210 moves from between the center portions 202 and 207 of the multi-grooves 201 and 206 and comes to be held between the end portions 203 and 209.

As mentioned above, the multi-grooves 201 and 206 are shallower from the center toward both ends, and the bottom surfaces of the multi-grooves are sloped with an inclination angle θ as seen in FIG. moves toward the ends of the multi-grooves 201 and 206, an axial force or thrust Q is generated that tries to move the two rotating members 200 and 205 apart, and this thrust Q is equal to the transmitted torque or load torque. The larger T becomes, the larger T becomes, and can be expressed by the following relational expression.

The thrust Q generated in this way becomes a pressing force between the friction wheels or between the friction wheels and a ring, etc., as described above, and generates a friction force according to the load torque T, so the friction wheels When the load torque is small, it moves easily relative to the other party, reducing power loss due to unnecessary friction and wear of the friction wheel, but when the load torque is large, the frictional force increases and slipping occurs. This makes it possible to transmit large torque.

[Problem to be solved by the invention]

Since the conventional self-adjusting pressure drum device has a structure as illustrated in FIG. 9 and FIG.
The intermediate position between each center B2O2 and 207 is shown in FIG. 9 by a solid line. ), but since a large number of pairs of balls 210 and grooves 201 and 206 that sandwich them are provided evenly around the axis 0, not all the balls 210 equally generate 0 thrust, The diameter of the ball 210 and the groove 201.
Due to a slight error in the shape of ball 206, there may be some playing balls that do not generate thrust Q. Since such an idle ball is not constrained by the bottom surface (slanted surface) of the groove 201, 206, it will take an indefinite position within its degree of freedom.

As is clear from FIG. 10, the ball 210 is
From the position 210a held between the center part 202 of the groove 201 and the end 209 of the groove 206 to the position 210b held between the center part 207 of the groove 206 and the end 203 of the groove 201. Since the ball 210 can exist in any position between 210a and 210b, due to some reason, not just an idle ball, the ball 210 may shift from its original position (the position shown by the solid line in FIG. 10). It is possible to approach the position of

If some of the multiple balls 210 are so misaligned, one rotating member 200 and the other rotating member 205 will no longer be parallel, and one will be tilted relative to the other. As a result, the state of engagement between many friction wheels and rings etc. is not uniform, resulting in friction wheels that slip abnormally, friction wheels that wear due to abnormally strong pressure contact, and friction wheels that are worn out due to abnormally strong pressure contact. and 205, those that are movable in the axial direction may not be able to slide smoothly in the axial direction due to inclination with respect to the axis, and the automatic regulating force device may not operate normally. obtain.

In order to solve this problem, the conventional self-adjusting pressure drum device in a friction-type continuously variable transmission maintains a large number of balls 210 at correct positions on the circumference between the two rotating members 200 and 2050. A known method is to insert a retainer (not shown) to prevent the balls 210 from taking a free position. However, using a retainer increases the number of parts, increases assembly man-hours, and changes the structure. This is by no means a good idea, as the complication leads to other problems such as increased costs.

The present invention addresses these problems and allows a large number of balls 210 to be placed in the correct position by extremely simple means without using a retainer in the automatically regulating pressure arm device in a compressor equipped with a friction-type continuously variable transmission. The purpose of this invention is to guide the system to ensure smooth operation, simplify the structure, and reduce costs.

[Means to solve the problem]

In order to solve the above problems, the present invention includes a compressor section that compresses fluid, at least one pair of friction wheels that engages with an output shaft for driving the compressor section, and an input shaft for the friction wheels. and a friction-type continuously variable transmission section that is integrally connected to the compressor section, and is arranged in series in a transmission system from the input shaft to the output shaft of the continuously variable transmission section. Cam grooves extending tangentially to an imaginary circle centered on the axis of rotation are provided on opposing surfaces of the two rotating members, and the ball is held between the cam grooves. The present invention provides a compressor with a transmission, characterized in that it is equipped with an automatically regulating pressure arm device for the engaging friction wheel formed by the above-described method.

[For production]

Since the compressor section is driven by the continuously variable transmission section, its driving rotational speed can be freely changed as necessary, and as a result, the amount of compressed fluid discharged can be changed steplessly.

Inside the continuously variable transmission section, a pair or more of friction wheels (including a gear change ring) that engage with each other are provided to transmit torque through frictional engagement. A self-adjusting force arm device is provided which applies pressure contact force to the friction wheel. In particular, the self-adjusting force arm device according to the present invention has two rotating members arranged in series in a transmission system extending from an input shaft to an output shaft. Cam grooves extending tangentially to an imaginary circle centered on the axis of rotation are provided on opposing surfaces, and the ball is held between the cam grooves, so that two When torque is transmitted between the two rotating members and a relative rotational angular displacement occurs between them, the pair of cam grooves assume an intersecting position, limiting where the ball can reside between them.

Therefore, the ball is no longer able to take a free position within each cam groove, and the ball naturally settles into its intended position. And between the pair of rotating members,
The action of the cam groove and the ball generates an axial thrust that corresponds to the size of the transmitted torque, that is, the size of the load, and this is transmitted to the friction wheel, which generates an overload force that corresponds to the size of the load at that time. Provides sufficient friction welding force.

Example] Embodiments of the present invention will be described based on the accompanying drawings.

As shown in a longitudinal cross-sectional view in FIG. 2, the compressor with a friction continuously variable transmission according to the present invention includes a friction-type continuously variable transmission (hereinafter simply referred to as a transmission) A and a compressor B. It is connected to

In the transmission A, reference numeral 1 denotes a human power shaft to which an input disk 2 is fitted and fixed, which is supported by a bearing 30 etc. and has a pulley 3 attached to one end. The rotational driving force is transmitted from 4 is an output shaft provided coaxially with the input shaft 1, and also serves as a drive shaft for the compressor B. Reference numeral 5 denotes an output disk, which is rotatably supported on the human-powered shaft 1 and connected to the output shaft via an automatic regulating force device 20, which will be described later.

Reference numeral 6 denotes a conical friction wheel called a planetary cone, which is installed around the axis X of the human power shaft 1 and the output shaft 4, and rotates and revolves around its own axis.By changing the revolution speed of the planetary cone 6,
The output shaft 4 can be driven by continuously changing the rotation speed from the input shaft 1. Reference numeral 7 denotes a housing of the transmission A, which is integrally fixed to the front side housing 101 of the compressor B by bolts (not shown).

The planetary cone 6 includes a conical portion 6a having an obtuse apex angle, a disk portion 6b coaxially provided integrally with the bottom surface of the conical portion 6a, and a disk portion 6b integrally provided at the center of the bottom surface of the disk portion 6b. and a mounting shaft 6c. The planetary cone 6 has three transmission surfaces. The first transmission surface 8 is the outer peripheral surface of the disk portion 6b, and its cross-sectional shape is concave so as to frictionally engage with the input disk 2. Second transmission surface 9
is a peripheral portion of the bottom surface of the conical portion 6a, which is a flat surface or a surface close to it, and is frictionally engaged with the output disk 5. The third transmission surface 10 is a conical surface of the conical portion 6a, and is frictionally engaged with a speed change ring 11, which will be described later. With the planetary cone 6 attached, the generatrix of the conical portion 6a on the side in contact with the speed change ring 11 is substantially parallel to the axis X.

The speed change ring 11 surrounds the plurality of planetary cones 6, is movable in the direction of the axis 11, but is non-rotatably supported by the housing 7, and is frictionally engaged with the third transmission surface 10 of the planetary cones 6. By reciprocating the control motor 29 in the direction of the axis X, the gear ratio can be changed steplessly. The planetary cone 6 is rotatably mounted on the carrier 12 via a mounting shaft 6C with a suitable clearance. The carrier 12 has a truncated cone shape, connects a plurality of planetary cones 6 to each other, and is rotatably provided around the axis X.

The speed change ring 11 is held by a ring holder 15,
The ring holder is attached so as to be movable in the axial direction along the guide pin 17. The ring holder 15 has an annular slot 15a that is open inward and has a U-shaped cross section.The speed change ring 11 is fitted into this annular slot 15a with a clearance fit, and the speed change ring 11 is axially aligned with respect to the ring holder 15. movement is prevented. A pin 19 is provided to prevent the speed change ring 11 from rotating relative to the ring holder 15.

A mechanism is known in which, by moving the ring holder 15 in a direction parallel to the axis X, the speed change ring 11 is moved in the same direction to change the speed change ratio. That is, the control motor 29
A rotating shaft 18 connected to the transmission axis extends in a direction perpendicular to the transmission axis X, and is threadedly engaged with the rotating shaft 18,
A rotationally prevented cam member (not shown) is provided, and this cam member is engaged with the cam surface of the ring holder 15.

Therefore, by rotating the control motor 29, the cam member is linearly moved in a direction intersecting the transmission axis X, and the cam drives the ring holder 15 in a direction parallel to the transmission axis X, thereby controlling the gear ratio. It is supposed to be done.

Reference numeral 20 denotes an automatic regulating force device which is a feature of the present invention, and includes a cam disk 21, the output disk 5 arranged opposite to this cam disk 21, and these cam disks 2.
A plurality of balls (
IIl record) consists of 22 pieces. As will be described in detail later, the output disk 5 and the cam disk 21 are movable relative to each other in the direction of the axis X, and the rotation of the output disk 50 is transmitted to the cam disk 21 by the ball 22. A compression spring 23 is also provided between the output disk 5 and the cam disk 21.
is arranged to constantly urge the output disk 5 toward the planetary cone 6. Thereby, a preload can be applied to each frictional engagement portion of the transmission 11A at the initial stage of rotation, and a frictional engagement force can be applied.

The output disk 5 and the hub 24 are connected and fixed by a plurality of bolts 25. The hub 24 is screwed and fixed to the screw 1ff14a at the tip of the output shaft 4.

In addition, a plurality of oil splashing pieces 21a are arranged on the outer periphery of the cam disc 21, and rotate with the rotation of the output shaft 4 to splash up the lubricating oil 26 accumulated in the oil reservoir portion 7a of the housing 7. Lubricate each sliding part.

Compressor B is a known wave plate type compressor. A disk-shaped wave plate L/-) 105 is attached to the drive shaft 104, which is an extension of the output shaft 4, so as to rotate integrally with the drive shaft 104, and both sides of the wave plate 1050 are provided with wave-shaped recesses and grooves along the circumferential direction. A convex portion is formed. The ends of cylinder 106 are closed by first and second valve plate assemblies 107,108. Two rollers 110 attached to a double-ended piston 109. 111
is rotatable about an axis J, and a wave plate 105 is sandwiched between these two rollers 110, 111.

In this way, a plurality of pistons 109 are arranged at regular intervals along the circumference of the wave plate 105, and each piston 109 can reciprocate left and right in the axis X direction.

The compressor drive shaft 104 is driven by the transmission A and rotates,
When the wave plate 105 rotates together with the wave plate 105, the piston 10
9 reciprocates in the axial direction. A cylinder chamber 112 that compresses fluid is connected to the piston 10 by the cylinder 106, the piston 109, and the first valve plate assembly 107.
9 is formed on both end sides. A high pressure chamber 113 and a low pressure chamber 114 are formed in the substantially annular front side housing 101, and the first valve plate assembly 1070 is attached to the cylinder 106 so as to press the peripheral edge of the first valve plate assembly 1070.

In the compressor with a continuously variable friction transmission according to the embodiment, the operation of the compressor is controlled by adjusting the gear ratio of the transmission according to the air conditioning load. The gear ratio is calculated from the current engine rotation speed so that the rotation speed of the manual shaft of the compressor can be obtained in accordance with the air conditioning load, and the rotation angle of the rotating shaft 18 of the control motor 29 is controlled according to the gear ratio. The position of the ring holder 15 along the axis X direction is determined according to this rotation angle. As a result, the axial position of the speed change ring holder 15 changes and the revolution speed of the planetary cone 6 changes, so that the rotation speed of the output shaft 4 changes. The gear ratio to the transmission can be controlled in this way, and the output of compressor B is thereby varied.

The self-regulating pressure dam device 20, which is a feature of the present invention, is shown in FIG.
It is shown in FIG. 3, FIG. 6, FIG. 7, etc. The automatic regulating force device 20 is composed of a pair of cam grooves 31 and 32 and the aforementioned ball (one ball) 22, but the shape of the cam groove 3L32 is different from that of the conventional one explained in FIGS. 9 and 10. It is clearly different from the one with a retainer.

In the illustrated embodiment, the cam groove 31 is provided on the back surface of the output disk 5, which is the first rotating member, and the planar shape of the groove is rectangular as seen in the above-mentioned drawings, and its longitudinal direction is aligned with the axis. Virtual circle 3 with radius γ centered on point 0 on X
Several similar cam grooves (six in the illustrated example) are provided at equal intervals on the circumference of the circle 33.

As seen in FIG. 5, the cam groove 31 is deep at the center 34 and becomes shallower toward the ends 35, 36, thereby forming inclined surfaces 37, 38. In the illustrated example, the cross-sectional shape of the cam groove 31 is symmetrical, but since the inclined surface 38 is not actually used, the ball 22
It may be a plane with an appropriate inclination or a curved surface with an appropriate shape that can stably hold the groove when it is at the deepest part (in the case of a symmetrical type, the center part) 34 of the groove 31.

On the other hand, the ball 22 is connected to the cam groove 31 of the output disk 5.
Another cam groove 32 facing each other with the cam groove 32 in between is formed on the surface of the cam disk 21, which is the second rotating member.

The shape of the cam groove 32 may be substantially the same as the cam groove 31 described above, and if the cam groove 31 is given a left-right asymmetric shape in FIG. 5, the cam groove 32 is also left-right asymmetric. , but its shape is ball 2
It will take a point-symmetrical shape with the center of 2 as the axis. In any case, the cross-sectional shape of the cam groove 32 should be given as the shape obtained when the cross-sectional shape of the cam groove 31 is rotated by 180° around the ball 22 as shown in FIG. In the illustrated example, therefore, the cam groove 32 also has a central portion 39, both end portions 40, 41, and sloped surfaces 42, 43.

The groove bottom surfaces of the cam grooves 31, 32 are flat as shown in FIG. 4, or may be cylindrical or other suitable curved surfaces as in the other embodiment shown in FIG.

In Fig. 8, cam grooves with curved bottom surfaces are shown at 31' and 32.
′.

In the case of the present invention, what is important is that the cam grooves 31 and 32 (3
1′ and 32′) δ A circle 33 whose longitudinal direction is radius γ
It should be arranged so that it coincides with the tangent line of . The width direction of the cam grooves 31 and 32 is formed to such a width and shape that there is not much play in the lateral direction when guiding the ball 22, respectively. The ball 22 is thereby guided relative to each disc 5 and 21 only in the direction tangential to the circle 33.

Since the cam grooves 31 and 32 are both oriented in the tangential direction of the circle 33, no torque is transmitted between the output disc 5 and the cam disc 21 when no load is applied to the transmission A. Since, there is no relative displacement in the direction of rotation,
As shown in FIG. 6, the cam groove 31 appears to overlap the cam groove 32. Then, a load acts on the transmission A, and both discs 5
When torque is transmitted between the cam grooves 31 and 21, and the two rotate relative to each other by an angle α mainly depending on the size of the clearance, the cam grooves 31 and 32 assume a crossed relationship position as shown in FIG. It turns out. Cam groove 31 and cam groove 32
In the state where the two cam grooves 31 intersect, the ball 22
, 32, the position of the ball 22 is determined naturally without using a retainer.

In FIG. 3, in a loaded state where the cams a31 and 32 intersect, the area where the two grooves overlap is shown as a hatched area. However, this does not mean that the ball 22 can exist anywhere within this shaded area, and due to the limited width of the cam grooves 31 and 32 (guiding action of the side walls of the cam grooves), the ball 22
settles approximately in the center of the shaded area. On the other hand, in the conventional example shown in FIGS. 9 and 10, the cam grooves 201 and 2
Since the ball 210 is arc-shaped and is provided along the circumference of a circle with a radius T, the ball 210 as shown in FIG.
Since the ball 22 can exist in a wide range from 210a to 210b, it has been necessary to use a spacing means such as a retainer, but in the example of the present invention, the position of the ball 22 can be corrected without using a retainer. It has the advantage of being fixed.

Because the cam grooves 31 and 32 are inclined, when torque is transmitted through the ball 22, the self-adjusting pressure ram device 20 generates a transmitted torque, that is, a thrust corresponding to the magnitude of the load. In this case, this thrust causes the output disk 5 to move axially to the left in FIG. 2 and is pressed against the second transmission surface 9 of the planetary cone 6, generating a frictional contact force on that surface. In addition, frictional contact force is also generated on the third transmission surface, which is the contact surface with the speed change ring 11 via the planetary cone 6, and on the first transmission surface, which is the contact surface with the human-powered disk 2.

[Effects of the invention] In the friction-type continuously variable transmission that is integrated into the compressor, by providing an automatically regulating pressure ram device with a new structure, the ball is held in a predetermined position only by a pair of cam grooves that sandwich it. Since the ball is held in the correct position, there is no need to provide a separate means such as a retainer for regulating the ball's position, and the mechanism becomes simple and costs can be reduced.

In addition, since the reliability of the transmission section is increased, there is no need to worry about connection with the compressor, and it can be used, for example, in vehicle air conditioners, and the discharge amount of compressed fluid can be freely and easily changed and adjusted. becomes possible.

[Brief explanation of the drawing]

Fig. 1 is a side view showing an embodiment of the entire automatic regulating force device for a transmission, which is a main part of the present invention, and Fig. 2 is a longitudinal sectional front view illustrating the overall configuration of the compressor with a transmission of this invention. , FIG. 3 is an enlarged partial view of a part of FIG. 1 in order to show the features of the automatic regulating force device, and FIG. 4 is a partial view of I'V-1'V in FIG. 3.
A sectional view, FIG. 5 is a V-V sectional view in FIG. 4, and FIG.
Figures 7 and 7 are diagrams showing different operating states, and Figure 8 shows different operating states.
9 is a sectional view showing another embodiment, FIG. 9 is a side view showing a conventional example, and FIG. 10 is a sectional view taken along line XX in FIG. 9. 1...Human power axis, 2...Input disk, 3
... Pulley, 4... A force shaft (compressor drive shaft), 5... Output disk, 6... Planetary cone (conical friction wheel), 7... Transmission housing, 8... ...First power transmission surface, 9...Second power transmission surface, 10
... Third transmission surface, 11 ... Speed change ring, 12
...Carrier, 15...Ring holder,
20... Automatic adjustment pressure dam device, 21... Cam disc, 22... Ball (@ball), 23... Compression spring,
24...Hub, 29...Control motor, 31.32.
...Cam groove, 33...Imaginary circle, 34...Central part, 35.36...End part, 37.38.
...Slope surface, 39...Central part, 40.41...
・End part, 42.43... Inclined surface, 101...
- Front side housing of compressor, 104... Drive shaft, 105... Wave plate, 106... Cylinder, 107, 108... Valve plate assembly, 109
...piston, 110. 111...Roller, 112...Cylinder chamber, 200...One rotating member, 201...Cam groove, 202...
Center part, -203, 204... End part, 20
5... Other rotating member, 206... Cam groove,
207...center part, 208, 209...end part,
210... Bonope 211... Center line,
A... Friction type continuously variable transmission, B... Compressor,
α...Difference angle, θ...Inclination angle, T
...Radius, Q...Thrust (pressing force), 0...Axis center, X...Axis line. Fig. 1 5...Output disk (first rotating member) 20...Automatic adjustment pressure dam device 21...Cam disc (second rotating member) 22...
Balls 31, 32...Cam groove tv-=-i Fig. 3 Fig. 4 Factor 5 20...Automatic adjustment pressure dam device 22...Balls 31, 32... Cam groove 8 Fig. 5. ...Output disk 20...Automatic adjustment pressure dam equipment! 21...Cam disc 22...Pole

Claims (1)

[Claims] A compressor unit that compresses fluid, a friction wheel that engages with an output shaft for driving the compressor unit, at least one pair of friction wheels, and an input shaft for the friction wheel, and is integrally fastened to the compressor unit. The friction-type continuously variable transmission section includes a friction-type continuously variable transmission section, and opposing surfaces of two rotating members arranged in series in a transmission system from the input shaft to the output shaft of the continuously variable transmission section include: Cam grooves extending tangentially to an imaginary circle centered on their axis of rotation are provided, and the engaging friction wheels are formed by sandwiching a ball between the cam grooves. A compressor with a transmission, characterized by being equipped with an automatically regulating pressure drum device.