Information
-
Patent Grant
-
6179595
-
Patent Number
6,179,595
-
Date Filed
Friday, May 14, 199925 years ago
-
Date Issued
Tuesday, January 30, 200123 years ago
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Inventors
-
Original Assignees
-
Examiners
Agents
-
CPC
-
US Classifications
Field of Search
US
- 418 102
- 418 104
- 418 166
- 418 170
- 418 171
- 418 2061
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International Classifications
-
Abstract
A hydraulic gear machine, particularly an internal-gear pump in a vehicular transmission, with an internal gear and an external gear, has a central bearing tube that rotatably supports the external gear and receives the input or output shaft of the transmission. The transmission shaft is rotatably supported in the bearing tube by means of a bearing that is radially interposed between the transmission shaft and the bearing tube.
Description
BACKGROUND OF THE INVENTION
The invention relates to a hydraulic gear machine such as a pump or motor, especially an internal-gear pump, external-gear pump, or similar device.
Hydraulic gear machines of this kind have become known through, e.g., DE-OS 2942417. Pumps of the type described therein are powered through a separate shaft driven by a drive motor. This configuration has the disadvantage that it requires the use of an additional element and takes up more space.
OBJECT OF THE INVENTION
One object of the present invention is to provide a hydraulic gear machine that has a small number of parts and saves as much space as possible.
SUMMARY OF THE INVENTION
In hydraulic gear machines according to the invention, the stated object is attained in that a central bearing tube is provided on which the second gear, e.g., a pinion, is rotatably supported, the bearing tube surrounds a transmission shaft of a vehicular transmission, and the transmission shaft is rotatably supported by a bearing that is radially interposed between the transmission shaft and the bearing tube. The bearing arrangement serves as the radially constraining support for the pump gear on one side and for the transmission shaft on the other.
As a practical design choice, the transmission shaft is the input shaft of the transmission. In a further embodiment, the practical choice may be that the transmission shaft is the output shaft of the transmission. Also, in a further embodiment it may be advantageous if the shaft is an intermediate shaft, such as, e.g., the intermediate shaft. The vehicular transmission may be a gear transmission such as a spur gear system or a planetary gear system. The vehicular transmission may also be a continuously variable transmission such as a cone-pulley transmission.
In this, it is particularly practical if the pinion, or in general a gear with external tooth profile, is driven by the transmission shaft.
It is practical, if one of the gears, such as the pinion, is non-rotatably connected to an annular element that has an internal tooth profile mating with an external tooth profile of the transmission shaft.
As a particularly advantageous feature, a seal such as a packing ring is arranged between the transmission shaft and the bearing tube.
It is further practical if the housing of the gear machine or pump is attached to the transmission housing. In this regard, it is advantageous in one embodiment if the housing of the gear machine is arranged on the inside of the transmission housing. In a further embodiment, it is practical if the housing of the gear machine is arranged on the outside of the transmission housing.
Further, it is particularly practical if a seal is interposed between the shaft and the transmission housing.
It is also advantageous if the bearing, e.g., a slide bearing or particularly a roller bearing, is connected to the source of lubricant for the pump or for the transmission through a lubricant-delivery element. In this regard, it is practical if the delivery of lubricant occurs through a connection such as a bore hole or channel that is formed or extends between a chamber filled with lubricant and the bearing. Likewise, it is practical if the lubricant-delivery element is configured as a channel from the bearing to a chamber containing lubricant.
In accordance with the invention it is particularly practical if the transmission shaft, e.g., the input shaft or output shaft of the transmission, passes axially through the bearing tube and interacts on one side with gear-shifting elements inside the transmission and on the other side has a drive connection, e.g., through a toothed profile.
The novel features that are considered as characteristic of the invention are set forth in particular in the appended claims. The improved apparatus itself, however, both as to its construction and its mode of operation, together with additional features and advantages thereof, will be best understood upon perusal of the following detailed description of certain presently preferred specific embodiments with reference to the accompanying drawing.
BRIEF DESCRIPTION OF THE DRAWINGS
The drawings serve to explain the invention in greater detail through examples, but are not meant to restrict in any way the general scope of the invention.
FIG. 1
represents a gear machine, e.g., a pump, in a fragmentary sectional view.
FIG. 2
represents a modified gear machine, e.g., a pump in a fragmentary, sectional view.
FIG. 3
represents the gear machine of
FIG. 1
in an elevational view.
FIG. 4
represents half of a section through a gear machine in accordance with the invention, and
FIG. 5
is a sectional view of a continuously variable transmission.
DETAILED DESCRIPTION OF THE INVENTION
FIGS. 1 and 3
represent a gear machine
1
, such as a pump, in which an internally toothed gear
2
and an externally toothed pinion
3
are rotatably arranged and supported in a cavity
4
(such as above) of a housing
5
. The pinion
3
is rotatably supported by means of a bearing tube
6
inside the housing
5
. A shaft
7
, such as a transmission shaft, passes through the bearing tube. The transmission shaft
7
has a connector element
8
such as an essentially annular flange element that is nonrotatably connected to the transmission shaft
7
and is also non-rotatably connected to the pinion
3
, so that the pinion
3
will rotate together with the transmission shaft
7
.
The flange element
8
has a toothed profile
8
a
at its inner radius or at least individual projections that engage a complementary toothed profile
9
or complementary recesses of the shaft
7
. At its outer radius, the flange element
8
has an external toothed profile
8
b
or projections that engage an internal toothed profile
10
or recesses, respectively, of the pinion
3
. Preferably, there are at least two projections
8
b
(three in the illustrated example) that engage corresponding recesses of the pinion.
A bearing device
11
, such as a roller bearing or slide bearing arrangement, is interposed between the pinion
3
and the bearing tube
6
(the latter being essentially non-rotatable relative to the transmission housing), with the roller elements of the roller bearing arrangement running directly on the outer circumference of the bearing tube
6
. Preferably, the bearing tube
6
is hardened to make it suitable for this purpose.
The transmission shaft
7
is rotatably supported inside the bearing tube
6
by means of the bearing
12
and in this case, too, the roller elements of the bearing run directly on the inside surface of the bearing tube. Thus, the bearing tube forms the running surface for the bearing rollers along both its inner and outer radius. The bearing tube
6
serves as supporting element for the transmission shaft
7
itself or for the bearing
12
that holds the transmission shaft. It is advantageous if the bearing
12
is configured as an antifriction bearing such as a roller bearing or needle bearing. In another embodiment, the bearing
12
may also be configured as a slide bearing.
In the design of the bearing
12
it is practical if the bearing is accommodated in a groove
7
b,
such as a circumferential groove, of the shaft
7
.
It is particularly advantageous if the bearing
12
is arranged in the axial area of the pump, particularly of the pump gears. In this case, the bearing
12
can take up the radially inward-directed forces of the pump that could cause an at least dynamic deformation of the bearing tube
6
. Thus, the dynamic radial forces of the pump are absorbed by the usually massive transmission shaft.
As an advantage of this configuration, the pump does not require an additional drive shaft. The motive power is supplied through the transmission shaft. In several advantageous applications of the invention, the transmission shaft can be supported in a way that no additional bearing device is required on the part of the pump. In these cases, the bearing arrangement comprising the bearing
12
and the bearing tube
6
is the only support of the shaft on the side of the motor or pump.
The delivery of lubricant, such as lubricating oil, to the bearing
12
is accomplished by connecting the bearing compartment to a pressure compartment
13
of the transmission. To achieve this connection, the seal, e.g., in the form of a packing ring
14
, that is used for sealing the rotationally nonconstrained passage of the shaft is arranged so that the bearing and the pressure compartment
13
are connected to each other and the seal
14
is not positioned between the pressure compartment
13
and the bearing
12
. To perform its function, the packing ring
14
is accommodated in a circumferential groove of the shaft
7
and in firm contact against the inside of the bearing tube. In the axial direction, the seal
14
is arranged between the bearing
12
and the flange
8
.
A seal
15
, e.g., in the form of a rotary shaft packing ring, seals the transmission shaft against the transmission housing.
It is advantageous to assemble the pump and its housing
5
of a plurality of components, at least of two axial plates
20
,
21
, and a central housing part
5
with a bore
4
. These components delimit and seal off the interior space of the pump where the gears are located, except for the connection
22
and the outflow opening
23
. For the connection (inlet) and outflow (outlet), channels
24
,
25
are provided in the transmission housing
40
.
In an advantageous arrangement, the axial plate
20
is accommodated in a recess
90
of the transmission housing
40
or the transmission housing cover, while the pump housing
5
is set back in relation to the axial plate
20
. As a result, with a given axial space allowance this portion of the transmission housing will have a greater wall thickness, which is appropriately used for accommodating the screw threads for attaching the pump
5
(not shown in the drawing).
It is particularly advantageous if the axial plates
20
,
21
are fixedly positioned in the pump housing
5
and/or the transmission housing
40
by means of at least two pins
91
,
92
. These pins are engaged, e.g., in bores or holes of the axial plates and housings. The fixation prevents the axial plates from being moved or rotated out of their correct position by friction forces.
It is also advantageous if at least one of the axial plates
230
,
231
is axially fixed in the area of the flange
202
(
FIG. 4
) and an abutment
32
(see FIG.
3
).
Between the two toothed profiles of the internally toothed hollow gear
2
and the externally toothed pinion
3
, there is a sickle-shaped cavity forming part of the bore
4
in which at least one filler body
31
, or a split filler body with the filler body parts, is arranged that abuts and/or is supported by an abutment pin
32
. The abutment pin traverses the cavity
4
and is preferably anchored in the axial plates, conveniently in bore holes. It is advantageous to provide a sealing element
33
between the filler body parts.
The pump housing
5
is attached, e.g., screwed, to the transmission housing
40
. At least one sealing gasket
41
is arranged between the pump housing and the transmission housing. As a means of attachment, the pump housing has bore holes (not shown) for bolts to pass through that are screwed into tapped holes in the transmission housing. Thus, the transmission housing does not have to be sealed because of attachment holes.
It is advantageous if the transmission shaft is the input shaft of the transmission because, as a rule, the latter turns at a higher rpm than the output shaft. In such embodiment, it is advantageous for the transmission input shaft to have a toothed profile
7
a
by which it is connected to a drive motor and for the toothed profile to be located outside of the transmission housing
40
. Alternatively, if the transmission shaft is the output shaft of the transmission, the toothed profile
7
a
serves to connect the transmission shaft to a further drive train arrangement of the vehicle.
FIG. 2
shows a further embodiment wherein a bearing
52
is arranged axially between a seal
51
and a flange or coupling element
53
, and the flange
53
is located axially between the seal
54
and the bearing
52
. To supply lubricant to the bearing from a low-pressure/high-pressure compartment
56
of the pump, a channel
57
is provided in the housing and a channel
58
in a bearing tube
59
so that the bearing is connected to the compartment
56
, which is preferably the low-pressure compartment. The coupling element
53
is conveniently held in place in the axial direction between the axial plate
20
and the pinion
3
.
It is particularly advantageous in a pump according to the invention that the bearing tube
6
can absorb transverse forces coming from the pump drive
7
.
FIG. 4
shows a half-section of a pump
201
exemplifying a gear machine where, in contrast to the embodiments of
FIGS. 1
to
3
, the flange
202
is not disk-shaped but has an L-shaped cross-section. The flange
202
has a radially extending portion
202
a
that is engaged at its outside radius in a toothed profile or in recesses of a pinion
203
. Furthermore, the flange has an axially extending portion
202
b,
where a seal
211
is arranged between said portion
202
b
and the housing
210
such as, e.g., a rotary shaft packing ring. At the opposite end from the portion
202
a,
the flange has an inward-facing toothed profile
202
c
engaging a toothed profile of the transmission shaft (not shown) that is accommodated inside the tube
204
. Thus, unlike in the arrangement illustrated in
FIG. 1
, the toothed profile
202
c
is not located inside the space that is closed off by the seal
211
.
The transmission housing
210
that supports the pump
201
is configured as a transmission cover that is attached to the actual transmission housing with fastening screws. Fastener holes
220
are provided for this purpose at an outer radius on the cover. Depending on the arrangement of the seals and of the bearing for the transmission shaft (not shown) inside the tube
204
, the inside of the transmission can lie either to the left or the right side of the transmission cover
210
in relation to the view shown in
FIG. 4
, i.e., the pump housing
205
can be arranged at the inside or outside of the transmission housing.
It is advantageous if the bearing tube
204
is a press fit in the pump housing
205
so that the contact surface between the housing and the bearing tube is sealed. In certain cases it is also possible to use a sealing element.
The design version of a continuously variable conepulley transmission partially represented in
FIG. 5
has on the input side a pair of disks (a disk set)
101
non-rotatably mounted on the driving shaft A and a pair of disks
102
non-rotatably mounted on the output shaft B. Each of the disk pairs has an axially movable disk-like part (conical flange)
101
a,
102
a,
respectively, and an axially fixed disk-like part (conical flange)
101
b,
102
b,
respectively. An endless loop means in the form of a chain or belt
103
is provided for transmitting torque between the two disk pairs.
In
FIG. 5
, the upper halves of the representation of the disk pair
101
and of the representation of the disk pair
102
show the respective relative axial positions of the disk-like parts
101
a,
101
b
and
102
a,
102
b
corresponding to the slow end of the transmission range (underdrive), while the lower halves of the same representations show the respective relative axial positions of the conical disk pairs
101
a,
101
b
and
102
a,
102
b
corresponding to the fast end of the transmission range (overdrive).
The disk pair
101
can be tightened in the axial direction through an actuator
104
configured as a piston/cylinder unit. In similar manner, the disk pair
102
can be axially tightened against the chain
103
through an actuator
105
, also configured as a piston/cylinder unit. In the pressure chamber
106
of the piston/cylinder unit
105
, an energy storing device
107
is provided in the form of a helical spring urging the axially movable disk
102
a
towards the axially fixed disk
102
b.
When, in the output part of the system, the chain
103
is in a radial position closer to the center of disk pair
102
, the tightening force applied by the energy storing device
107
is greater than when the chain
103
is in a radial position farther from the center of disk pair
102
. This means that as the transmission ratio is increased towards a faster output, the force applied by the energy storing device
107
also increases. One end convolution of the helical spring
107
bears directly against the axially movable disk
102
a
and at the other end convolution bears against a cup-shaped component
108
that bounds the pressure chamber
106
and is rigidly connected with the output shaft B.
Acting in parallel with the piston/cylinder units
104
and
105
, respectively, additional piston/cylinder units
110
and ill are provided for the purpose of varying the transmission ratio. The pressure chambers
112
,
113
of the piston/cylinder units
110
,
111
can be alternatively filled with or can discharge pressure medium according to the required transmission ratio. For this purpose, the pressure chambers
112
,
113
in accordance with requirements can be connected either to a source of a pressure medium such as a pump or else to an outlet channel. Thus, when the transmission ratio is to be changed, one of the pressure chambers
112
,
113
is filled with pressure medium, i.e., its volume is increased, while at the same time the other of the pressure chambers
112
,
113
is at least partially emptied, i.e., its volume is reduced. This alternating pressurizing of fluid in and emptying of pressure chambers
112
and
113
, respectively, can be performed by means of a suitable valve. Concerning the design and the function of this kind of a valve, reference is made in particular to the aforementioned existing state of the art.
To generate an at least torque-dependent pressure, a torque sensor
114
is provided, whose function is based on a hydromechanical principle. The torque, which is introduced through a driving gear or driving pinion
115
, is transmitted by the torque sensor
114
to the conical disk pair
101
. The driving gear
115
is mounted on the driving shaft A by way of a roller bearing
116
and has a form-locking connection or toothed profile
117
, causing it to share its rotation with the cam disk
118
of the torque s-ensor
114
that also bears against the driving gear
115
in the axial direction. The torque sensor
114
has the axially fixed cam disk
118
and an axially movable cam disk
119
, both of which have sloped ramps, with spreading bodies in the form of balls
120
arranged between the ramps to spread the cam disks apart. The cam disk
119
is movable in the axial direction along the shaft A but is constrained to rotate together with the latter. For this purpose, the cam disk
119
has a portion
119
a
facing in the opposite axial direction from the balls
120
as well as facing outward in the radial direction and carrying a toothed profile
119
b
engaged in a complementary toothed profile
121
a
of a component
121
. The latter has a fixed connection preventing both axial as well as rotational motion of the component
121
in relation to shaft A. At the same time, the toothed profile
119
b
and the complementary profile
121
a
are shaped in relation to each other in a manner that will allow an axial displacement between the components
119
and
121
.
The components of the torque sensor
114
define two pressure compartments
122
,
123
. The pressure compartment
122
is bounded by a ring-shaped component
124
that is rigidly connected to the driving shaft A, as well as by portions or components
125
,
126
that are formed on or attached to the cam disk
119
. The ring-shaped pressure compartment
123
is arranged at a greater radius than the ring-shaped pressure compartment
122
but is offset from the latter in the axial direction. The second pressure compartment
123
, too, is bounded by the ringshaped component
124
and also by the sleeve-like component
121
and further by the ring-shaped component
125
, which latter has a fixed connection to cam disk
119
, is axially movable, and functions as a piston.
The input shaft A, which carries the torque sensor
114
and the conical disk pair
101
, is supported inside a housing
130
by a needle bearing
127
at the end near the torque sensor
114
and at the opposite side of the conical disk pair
101
by a ball bearing
128
taking up the axial forces and a roller bearing
129
taking up radially directed forces. At the shaft end adjacent to the actuators
105
and
111
, the driven shaft B that carries the driven disk pair
102
is supported in the housing
130
by a dual-taper roller bearing
131
that takes up forces in the radial as well as both axial directions. On the opposite side (relative to the location of actuators
105
and
111
) of the disk pair
102
, the driven shaft B is supported in the housing
130
by a roller bearing
132
. The driven shaft B at the far end relative to actuators
105
and
111
carries a bevel gear
133
that is operatively connected to, e.g., a differential.
The pressure that is modulated by the torque sensor
114
at least as a function of the torque, as required for tightening the continuously variable cone-pulley transmission, is generated by a pump
134
(PI). Through a tube
135
inside shaft A having at least two chambers and leading to at least one radial channel
136
, the pump
134
communicates with the pressure compartment
122
of the torque sensor
114
. The pump
134
is further connected via a connecting conduit
137
with the pressure chamber
106
of the piston/cylinder unit
105
associated with the second disk pair
102
. The connecting conduit
1
˜
7
leads to a tubular-shaped channel
138
with at least two chambers formed by web portions inside the driven shaft B. The hollow pipe
138
, in turn, leads to the pressure chamber
106
via at least one radially oriented channel
139
.
The pressure compartment
122
of the torque sensor
114
communicates with the pressure chamber
109
of the piston/cylinder unit
104
via the channel
140
, which is offset in the circumferential direction relative to the sectional plane of FIG.
5
and is therefore indicated by broken lines. The channel
140
runs through the ring-shaped component
124
that is rigidly connected to shaft A. Thus, there is a permanent connection between the first pressure compartment
122
and the pressure chamber
109
. The driving shaft A is further provided with at least one outlet channel
141
that is connected, or can be connected, with the pressure compartment
122
and whose outlet cross-section is variable as a function of at least the transmitted torque. The outlet channel
141
opens to a central axial bore
142
of shaft A which, in turn, may be connected to a conduit that allows the oil drained from the torque sensor to be directed to locations where it may be used for the lubrication of component parts. The inner portion
126
a
of the ramp disk or cam disk
119
that is supported in an axially movable connection on the driving shaft A forms a closure means for the outlet channel
141
that can close off the outlet channel
141
to a greater or lesser extent dependent on at least the torque that prevents at the particular instant. Thus, the closure means
126
a
in combination with the outlet channel
141
forms a valve, or more precisely, a throttle. Depending at least upon the torque existing between the two cam disks
118
and
119
, the outlet opening or the outlet channel
141
is opened or closed to a commensurate degree by the disk
119
acting as a control piston, whereby an amount of pressure originating from the pump
134
and corresponding to at least the momentarily existing torque is introduced at least into the pressure compartment
122
. Because the pressure compartment
122
is connected to the pressure chamber
109
and also communicates with the pressure chamber
106
via the channels or conduits
135
,
136
,
137
,
138
and
139
, a corresponding pressure is generated also in pressure chambers
109
and
106
.
Because the piston/cylinder units
104
,
105
are arranged in parallel with the piston/cylinder units
110
,
111
, the forces arising from the pressure delivered by the torque sensor
114
and acting on the axially movable disks
101
a,
102
a
are added to the forces bearing against the axially movable disks
101
a,
102
a
due to the pressure in the chambers
112
,
113
that serves to set the transmission ratio.
The pressure chamber
112
is supplied with pressure medium through a channel
143
provided inside the shaft A, which through a radial bore hole
144
is connected to an annular groove
145
on shaft A. Starting from the annular groove
145
, at least one channel
146
traverses the ring-shaped component
124
and forms a connection to the radial passageway
147
traversing the sleeve-shaped component
121
and opening to the pressure chamber
112
. In a similar manner, the pressure chamber
113
, too, is supplied with oil, namely via the channel
148
that surrounds the channel
138
and communicates through radially directed connector channels
149
with the pressure chamber
113
. The channels
143
and
148
are supplied from a common pressure source through connecting conduits
151
,
152
with at least one valve
150
arranged between them. The pressure source
153
that is connected to the valve
150
or valve system
150
can constitute a separate pump, or else it can also be the already existing pump
134
, in which case an appropriate volumeor pressure-distributing system
154
is required, which may comprise a plurality of valves. This alternative solution is indicated with a broken line.
In the relative position of the individual components as shown in the upper half of the representation of the disk pair
101
, the pressure compartment
123
, whose pressure supply effectively parallels the pressure compartment
122
, is separated from a pressure supply, the reason being that the channels or bore holes
155
,
156
,
157
,
158
,
159
,
160
that communicate with the pressure compartment
123
are not connected with a source of pressure medium such as, in particular, the pump
134
. In the illustrated position of the axially movable disk
101
a,
the radial bore hole
160
is fully open so that the compartment
123
is fully relieved from pressure. The axial force acting on the cam disk or ramp disk
119
that is generated by the torque to be transmitted is taken up only through the oil pressure cushion building up in the pressure compartment
122
. In this, the higher the pressure in pressure compartment
122
is at a given time, the higher the amount of torque to be transmitted. As already mentioned, this pressure is controlled by the inner portion
126
a
of cam disk
119
and the outlet bore hole
141
acting together as a throttle valve.
When the transmission ratio is to be increased, the conical disk
101
a
is moved to the right in the direction towards the conical disk
101
b.
This has the effect on the conical disk pair
102
that the conical disk
102
a
will back up from the axially fixed conical disk
102
b.
As already mentioned, the upper halves of the representations of the conical disk pairs
101
,
102
illustrate the relative positions between the conical disks
101
a,
101
b
and
102
a,
102
b
corresponding to the slow end of the transmission range, while the lower halves of the same representations illustrate the relative positions between the conical disks
101
a,
101
b
and
102
a,
102
b
corresponding to the fast end of the transmission range.
In order to shift from the transmission ratio of the conical disk pairs
101
,
102
illustrated in the upper halves of the representations to the transmission ratio illustrated in the respective lower halves, the valve
150
is regulated so as to fill the pressure chamber
112
and to empty or commensurately reduce the volume of pressure chamber
113
.
The axially displaceable conical disks
101
a,
102
a
are non-rotatably coupled to their respective associated shafts A and B through connections
161
,
162
by means of splines. The connections
161
,
162
formed by spline fittings on the disks
101
a,
102
a
and by outward-facing splines on the shafts A and B allow the disks to move in the axial direction along the respective shafts A, B while constraining the disks to rotate together with the respective shafts A, B.
The position of the axially displaceable disk
101
a
and of the chain
103
as shown in dash-dotted lines in the upper half of the representation of the driving disk pair
101
corresponds to the fastest possible transmission ratio. The position of the chain
103
and disk set
101
drawn in dash-dotted lines corresponds to the position of the chain
103
as drawn in solid lines in the lower half of the representation of the driven disk pair
102
.
The position of the axially displaceable disk
102
a
and of the chain
103
as shown in dash-dotted lines in the lower half of the representation of the driven disk pair
102
corresponds to the slowest possible transmission ratio. This position of the chain
103
corresponds to the position of the chain
103
drawn in solid lines in the upper half of the representation of the first disk set
101
.
In the embodiment shown, the conical disks
101
a,
102
a
at their inside radii are provided with centering guide portions
163
,
164
and
165
,
166
, respectively, by which they are in immediate contact with and centered on the respective shafts A and B. The centering guide portions
163
,
164
of the axially displaceable disk
101
a,
contacting the outer surface of shaft A practically without radial play, in combination with the channels
159
,
160
are functioning as valves in which the disk
101
a
in relation to the channels
159
,
160
effectively serves as the valve gate. When the disk
101
a
is displaced to the right from the position shown in the upper half of the representation of the disk set
101
, after a certain amount of travel the channel
160
is gradually closed off by the centering guide portion
164
as the axial displacement of the disk
101
a
increases. In other words, the centering guide portion
164
is now positioned in the radial sense above the opening of channel
160
. In this position, the channel
159
, too, is closed off at its outer radial end by the conical disk
101
a,
i.e., by the centering guide portion
163
. As the disk
101
a
is moved further in the axial direction towards the disk
101
b,
the channel
160
remains closed while on the other hand the disk
101
a,
i.e., its centering guide portion
163
, gradually opens the channel
159
. Thereby a connection is established between the pressure chamber
109
of the cylinder/piston unit
104
and the channel
158
via the channel
159
whereby, in turn, a connection to the pressure compartment
123
is made via channels
157
,
156
and
155
. Given that the channel
160
is effectively closed and a connection now exists between the pressure chamber
109
and the two pressure compartments
122
and
123
, the pressure (except for small losses that may occur in the connecting path) will effectively be equalized between the two pressure compartments
122
,
123
and the pressure chamber
109
and thus also in the chamber
106
, the latter being effectively connected with the compartments
122
,
123
and the chamber
109
through the channel
135
and the conduits
137
,
138
. As the two pressure compartments
122
and
123
are connected to a degree that depends on the transmission ratio, the effective axially facing surface of the pressure cushion in the torque sensor
114
is increased because the combined effects of the axially facing surfaces of the two pressure compartments
122
,
123
are additive. Due to this increase in the effective axially directed thrust surface, the amount of pressure generated by the torque sensor in relation to a given amount of torque is reduced essentially in proportion to the surface increase which, in turn, means that a corresponding decrease in pressure is also found in the pressure chambers
109
and
106
. Accordingly, by means of the inventive torque sensor
114
, it becomes possible to effect a transmission-ratio-dependent modulation of the pressure that is superimposed on the torque-dependent modulation of the pressure. The torque sensor
114
as described allows, in effect, a two-stage modulation of the amount or level of pressure.
In the embodiment described, the two channels
159
,
160
in relation to each other and in relation to the portions
163
,
164
of the disk
101
a
that interact with the channels
159
,
160
are arranged or configured in such a manner that the shift from the one pressure compartment
122
to both pressure compartments
122
,
123
and vice versa occurs at a transmission ratio of the continuously variable cone-pulley transmission of approximately 1:1. As indicated previously, due to the design configuration it is not possible for a shift of this kind to occur abruptly, meaning that there is a transition range where on the one hand the outlet channel
160
is already closed but on the other hand the connector channel
159
is not yet connected to the pressure chamber
109
. In order to ensure the function of the transmission, i.e., of the torque sensor
114
, in this transition range, which requires providing a possibility for the cam disk
119
to be moved along the axial direction, there are equalizer means provided to allow the volume of the pressure compartment
123
to be changed so that the torque sensor
114
can perform its pump action, meaning that the cylinder components and the piston components of the torque sensor
114
can move relative to each other in the axial direction. In the embodiment shown, the aforementioned equalizer means are provided in the form of a sealing tongue or lip
167
, which is seated in a radial groove of the ring-shaped component
124
and interacts with the inner cylinder surface of the component
125
in order to seal the two pressure compartments
122
,
123
in relation to each other. The seal ring
167
is shaped and arranged in such a manner that it blocks passage, i.e., prevents pressure equalization between the compartments
122
and
123
, only in one axial direction while permitting pressure equalization, i.e., passage of the seal ring
167
, to occur in the opposite direction at least as long as there is a positive pressure differential between the pressure compartment
123
and the pressure compartment
122
. Thus, the seal ring
167
acts not unlike a check valve in that the flow from the pressure compartment
122
to the pressure compartment
123
is blocked while passage through the seal formed by the seal ring
167
is possible when there is a certain amount of overpressure in the pressure compartment
123
relative to the pressure compartment
122
. Accordingly, when the ramp disk
119
moves to the right, pressure fluid is allowed to flow from the closed-off pressure compartment
123
into the pressure compartment
122
. If the cam disk
119
is subsequently moved to the left, an underpressure may develop in the pressure compartment
123
, including even the possibility of air bubbles forming in the oil. However, this is not harmful to the function of the torque sensor or to the continuously variable cone-pulley transmission.
Instead of the seal
167
functioning as a check valve, one could also provide an actual check valve between the two pressure compartments
122
,
123
that would be installed in the ring-shaped component
124
. In such case, it would be possible to use a seal
167
that works in both axial directions. Further, the check valve referred to above could also be-arranged in such a manner that it would act between the two channels
135
and
158
. In this case, the check valve has to be installed in such a way that a volumetric flow is possible in the direction from the pressure compartment
123
to the pressure compartment
122
, but the flow of fluid is blocked in the opposite direction.
As can be seen from the preceding description of the operation, practically over the entire part of the range where the transmission effects a speed reduction (underdrive), the axial force transmitted between the ramps of the cam disks
118
,
119
bears against the effective axial thrust surface formed by the pressure compartment
122
alone. In contrast, practically over the entire part of the range where the transmission effects a speed increase (overdrive), the axial force transmitted between the ramps of the cam disks
118
,
119
bears against both of the effective axial thrust surfaces formed by the pressure compartments
122
,
123
. Thus, in relation to a given input torque, the pressure generated by the torque sensor
114
is higher when the transmission works in a speed-reducing mode than when it works in a speed-increasing mode. As already mentioned, the transmission described here is configured in such a manner that the switch-over point where a connection or separation between the pressure compartments
122
,
123
occurs is in the vicinity of a transmission ratio of approximately 1:1. However, it is possible to change the location of the switch-over point or the switch-over range within the overall range of the cone-pulley transmission through an appropriate arrangement and configuration of the channels
159
,
160
and of the portions
163
,
164
of the conical disk
101
a
that interact with the channels
159
,
160
.
The establishment or interruption of communication between the two pressure compartments
122
,
123
can also be accomplished by providing for this purpose a special valve that may be arranged in combination with a channel connecting the two pressure compartments
122
,
123
where, in addition, this valve need not be controllable directly via the disk
101
a
or
102
a
but may be actuated, e.g., from an external energy source. An electromagnetically, hydraulically, or pneumatically actuable valve that can be switched dependent on the ratio or change in the ratio of the transmission may be used for this purpose. As an example, a so-called 3/2 valve effecting a connection or separation between the two pressure compartments
122
,
123
could be employed. However, it is also possible to use pressure valves. A suitable valve of this kind could be arranged in combination with a conduit connecting the two channels
135
and
158
, with the two channels
159
and
160
being closed off or omitted in this case. The valve in this arrangement is oriented and connected in such a manner that in the case where the pressure compartments
122
,
123
are separated, the valve provides pressure relief to the pressure compartment
123
. For this purpose, the valve may be connected to a conduit leading back to the oil sump.
When an externally controllable valve is employed, it becomes possible to also actuate the valve dependent on other parameters. Thus, the valve could also be made to operate dependent on abrupt changes in the driving torque. Thereby, slippage of the chain belt can be avoided or in any case reduced, at least under certain operating conditions or in certain stages of the transmission range of the cone-pulley transmission.
In the design configuration shown in
FIG. 5
, the torque sensor
114
is arranged on the driving side and adjacent to the axially displaceable conical disk
101
a.
However, the torque sensor
114
may be arranged at and adapted to any arbitrary point in the flow path of the torque. Thus, as is known per se, a torque sensor
114
can also be arranged on the driven side, i.e., on the driven shaft B. A torque sensor of that kind may then be placed adjacent to the axially movable conical disk
102
a
in a similar manner as the torque sensor
114
. As is further known, it is also possible to use a plurality of torque sensors. Thus, for example, a suitable torque sensor may be arranged both on the driving side and on the driven side.
Also, the torque sensor
114
may be combined with at least two pressure compartments
122
,
123
, using other essentially known undertakings to modulate the pressure dependent on the torque and/or dependent on the transmission ratio. Thus, for example, the rolling elements
120
could be displaceable, dependent on a change in the transmission ratio, in the radial direction along the ramps or paths that interact with the rolling elements, similar to the arrangement described in the publication DE-OS 42 34 294.
In the embodiment according to
FIG. 5
, the pressure chamber
106
is connected to the torque sensor
114
. However, the pressure delivered by the torque sensor
114
may also be supplied to the exterior pressure chamber
113
, in which case the interior pressure chamber
106
serves the purpose of changing the transmission ratio. To accomplish this, one only has to interchange the connections of the two conduits
152
and
137
to the second disk set
102
.
In the embodiment of the torque sensor
114
according to
FIG. 5
, the components of the torque sensor are made largely of sheet metal. Thus, particularly the ramp disks
118
and
119
can be made as sheet metal stampings, e.g., by press-forming. To control the pressure in the individual pressure chambers, valves V, are provided at least in individual cases where appropriate, with a pressure medium being supplied to the valves from a pump P, through hydraulic conduits
90
.
Without further analysis, the foregoing will so fully reveal the gist of the present invention that others can, by applying current knowledge, readily adapt it for various applications without omitting features that, from the standpoint of prior art, fairly constitute essential characteristics of the generic and specific aspects of the aforedescribed contribution to the art and, therefore, such adaptations should and are intended to be comprehended within the meaning and range of equivalence of the appended claims.
Claims
- 1. A hydraulic gear machine for use in a vehicle with a transmission and a transmission shaft, comprising a gear machine housing, a first gear, a second gear, a central bearing tube, and a bearing, wherein the first gear is rotatably journalled in the gear machine housing, the bearing tube rotatably supports the second gear and receives the transmission shaft, and the transmission shaft is rotatably supported in the bearing tube by means of the bearing, the bearing being radially interposed between the transmission shaft and the bearing tube.
- 2. The hydraulic gear machine of claim 1, wherein the hydraulic gear machine is an internal-gear pump, the first gear is an internal gear, and the second gear is a pinion.
- 3. The hydraulic gear machine of claim 1, wherein the transmission has an input shaft and an output shaft and said transmission shaft is the input shaft of the transmission.
- 4. The hydraulic gear machine of claim 1, wherein the transmission has an input shaft and an output shaft and said transmission shaft is the output shaft of the transmission.
- 5. The hydraulic gear machine of claim 1, further comprising a seal that is interposed between the transmission shaft and the bearing tube.
- 6. The hydraulic gear machine of claim 1, wherein the transmission shaft extends axially through the bearing tube.
- 7. The hydraulic gear machine of claim 1, wherein the second gear is driven by the transmission shaft.
- 8. The hydraulic gear machine of claim 7, further comprising an annular element having a toothed internal profile, the transmission shaft having a toothed external profile mating with said internal profile, wherein the second gear is non-rotatably connected to the annular element.
- 9. The hydraulic gear machine of claim 1, wherein the transmission has a transmission housing and the gear machine housing is attached to the transmission housing.
- 10. The hydraulic gear machine of claim 9, wherein the transmission housing has an inside and the gear machine housing is arranged at the inside of the transmission housing.
- 11. The hydraulic gear machine of claim 9, wherein the transmission housing has an outside and the gear machine housing is arranged at the outside of the transmission housing.
- 12. The hydraulic gear machine of claim 9, further comprising a seal that is interposed between the transmission shaft and the transmission housing.
- 13. The hydraulic gear machine of claim 1, further comprising a lubricant-delivery element, the vehicle having a source of lubricant for at least one of the hydraulic gear machine and the transmission, wherein the lubricant-delivery element connects the bearing to the source of lubricant.
- 14. The hydraulic gear machine of claim 13, wherein the source of lubricant has a chamber and the lubricant-delivery element comprises a channel leading from the bearing to said chamber.
Priority Claims (1)
Number |
Date |
Country |
Kind |
198 23 633 |
May 1998 |
DE |
|
US Referenced Citations (1)
Number |
Name |
Date |
Kind |
5263818 |
Ito et al. |
Nov 1993 |
|
Foreign Referenced Citations (1)
Number |
Date |
Country |
3410015 |
Sep 1985 |
DE |